JP2021134823A - Vibration control device for rotary machine, pump installation and method for adjusting vibration control device for rotary machine - Google Patents

Abstract

To prevent deformation of an elastic support part due to settling of an elastic material and misalignment of a rotary machine while securing vibration control performance.SOLUTION: A vibration control device 60 includes: a vibration control base 61 subjected to load from a speed reducer; an elastic support part 70 for supporting the vibration control base 61; and a slide support part 80 for supporting the vibration control base 61, restricting a strain amount of the elastic support part 70 in a longitudinal direction to a certain amount and capable of laterally sliding in accordance with lateral vibration of the vibration control base 61.SELECTED DRAWING: Figure 3

Description

The present invention relates to a vibration isolator for a rotating machine, pump equipment, and a method for adjusting a vibration isolator for a rotating machine.

The following Patent Document 1 discloses a vibration isolator for a rotating machine. This vibration isolator provides vibration isolation for the support pedestal that supports the speed reducer (rotary machine) of the pump equipment. The vibration isolator is basically composed of an elastic support portion using an elastic material such as rubber, and absorbs the vibration of the rotating machine by the elasticity of the elastic material.

Japanese Patent No. 5670766

By the way, in the above-mentioned anti-vibration device, since the elastic material is settled in the vertical direction, there is a problem of workability and secular change due to the settling. Since the settling is a characteristic of the elastic material, the only way to solve it fundamentally is to replace the elastic material regularly or to use a material without the settling. When the sagging occurs, the elastic support portion is deformed, which makes it difficult to align the rotating machine mounted on the vibration isolator. For this reason, conventionally, a structure that can tolerate misalignment due to sagging has been dealt with by incorporating it into, for example, a shaft joint.

The present invention has been made in view of the above problems, and an object of the present invention is to prevent deformation of the elastic support portion and misalignment of the rotating machine due to sagging of the elastic material while ensuring anti-vibration performance.

The anti-vibration device for a rotating machine according to one aspect of the present invention includes an anti-vibration pedestal that receives a load from the rotating machine, an elastic support portion that supports the anti-vibration pedestal, and the elastic support portion that supports the anti-vibration pedestal. In addition to limiting the amount of vertical deflection of the vibration isolator to a certain amount, it is provided with a slip support portion that can skid according to the lateral vibration of the anti-vibration pedestal.

The anti-vibration device of the rotating machine may include a level adjusting portion for adjusting the support height of the anti-vibration pedestal in the slip support portion.

The vibration isolator of the rotating machine may include a deflection amount adjusting portion for adjusting the initial deflection amount in the vertical direction of the elastic support portion.

The anti-vibration device of the rotating machine includes a measuring unit that measures at least one of a load and a vibration applied to at least one of the anti-vibration stand, the elastic support portion, and the sliding support portion. You may.

The vibration isolator of the rotating machine may include a detecting unit that detects an abnormality or a sign of the abnormality of the rotating machine based on the measurement result of the measuring unit.

Further, the pump equipment according to one aspect of the present invention includes the vibration isolator described above, a rotating machine supported by the vibration isolator, and a pump assembly connected to the rotating machine.

The pump equipment may include an edge foundation that surrounds the installation area of the anti-vibration device, and a bulky portion that arranges the anti-vibration device at a height higher than or higher than the edge foundation.

The pump equipment may be provided with a foundation without an edge foundation that surrounds the installation area of the vibration isolator.

Further, the method of adjusting the anti-vibration device of the rotating machine according to one aspect of the present invention is to support the anti-vibration pedestal that receives the load from the rotating machine, the elastic support portion that supports the anti-vibration pedestal, and the anti-vibration pedestal. The amount of vertical deflection of the elastic support portion is limited to a certain range, and the slip support portion capable of skidding according to the lateral vibration of the anti-vibration gantry and the support height of the anti-vibration gantry in the slip support portion. A method for adjusting a vibration isolator of a rotating machine, comprising a level adjusting unit for adjusting the sag and a deflection amount adjusting unit for adjusting the initial deflection amount in the vertical direction of the elastic support portion, wherein the deflection amount adjusting unit is provided. A first step in which a load is not applied to the elastic support portion, and a second step in which the level adjusting portion adjusts the support height of the anti-vibration pedestal in the slip support portion after the first step. After the second step, there is a third step of adjusting the initial vertical deflection amount of the elastic support portion by the deflection amount adjusting portion.

According to the above aspect of the present invention, it is possible to prevent deformation of the elastic support portion due to sagging of the elastic material and misalignment of the rotating machine while ensuring anti-vibration performance.

It is an overall block diagram of the pump equipment which concerns on 1st Embodiment. It is a plane block diagram of the vibration isolation system which concerns on 1st Embodiment. It is sectional drawing of the vibration isolation device (the first vibration isolation device) which concerns on 1st Embodiment. It is explanatory drawing of the adjustment method of the vibration isolation device which concerns on 1st Embodiment. It is explanatory drawing of the adjustment method of the vibration isolation device which concerns on 1st Embodiment. It is explanatory drawing of the operation principle of the vibration isolation device which concerns on 1st Embodiment. It is a graph which shows an example of the measurement result of the measurement part which concerns on 1st Embodiment. It is sectional drawing which shows one modification of the vibration isolation device (first vibration isolation device) which concerns on 1st Embodiment. It is sectional drawing which shows one modification of the vibration isolation device (first vibration isolation device) which concerns on 1st Embodiment. It is sectional drawing which shows one modification of the vibration isolation device (first vibration isolation device) which concerns on 1st Embodiment. It is sectional drawing which shows one modification of the vibration isolation device (first vibration isolation device) which concerns on 1st Embodiment. It is sectional drawing which shows one modification of the vibration isolation device (first vibration isolation device) which concerns on 1st Embodiment. It is sectional drawing which shows one modification of the vibration isolation device (first vibration isolation device) which concerns on 1st Embodiment. It is sectional drawing which shows one modification of the vibration isolation device (first vibration isolation device) which concerns on 1st Embodiment. It is sectional drawing which shows one modification of the vibration isolation device (first vibration isolation device) which concerns on 1st Embodiment. It is sectional drawing which shows one modification of the vibration isolation device (first vibration isolation device) which concerns on 1st Embodiment. It is sectional drawing which shows one modification of the vibration isolation device (first vibration isolation device) which concerns on 1st Embodiment. It is sectional drawing which shows one modification of the vibration isolation device (first vibration isolation device) which concerns on 1st Embodiment. It is a plane block diagram of the vibration isolation system which concerns on 2nd Embodiment. It is sectional drawing of the vibration isolation device (second vibration isolation device) which concerns on 2nd Embodiment. It is a plane block diagram of the vibration isolation system which concerns on 3rd Embodiment. It is sectional drawing of the vibration isolation device (third vibration isolation device) which concerns on 3rd Embodiment.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings.

(First Embodiment)
FIG. 1 is an overall configuration diagram of the pump equipment 1 according to the first embodiment.
The pump equipment 1 shown in FIG. 1 includes a drive machine 10, a speed reducer 20 (rotary machine), and a pump assembly 30. The pump assembly 30 is a so-called vertical pump. The drive unit 10 and the speed reducer 20 are installed on the first floor 2A of the building foundation 2 (foundation). Further, the pump assembly 30 is installed on the second floor 2B of the building foundation 2.

The drive unit 10 is composed of a diesel engine, a gas turbine, a motor, and the like. The drive shaft 11 of the drive machine 10 extends in the horizontal direction and is connected to the speed reducer 20 via a shaft joint 12. The speed reducer 20 is a so-called orthogonal speed reducer, which is supported by a vibration isolation system 50 (described later) installed on the first floor 2A directly above the pump casing 31 of the pump assembly 30, and exerts the rotational force of the drive machine 10. It is provided with an output shaft 21 that decelerates and transmits to the pump rotation shaft 32 vertically below.

The pump rotating shaft 32 extends from the shaft penetrating portion 33 at the upper part of the pump casing 31 to the outside and upper side of the pump casing 31, and is connected to the output shaft 21 of the speed reducer 20 via the shaft joint 22. In the shaft penetrating portion 33, the pump rotating shaft 32 is rotatable, but is sealed so that pumping water or drainage inside the pump casing 31 does not leak to the outside of the pump casing 31.

The pump casing 31 has a suspension casing 34 which is substantially cylindrical and is arranged with its cylindrical axis vertical, a discharge elbow 35 which is connected above the suspension casing 34 and bends the flow direction in the horizontal direction, and a suspension casing. A discharge bowl 36 connected below the 34 and having a guide blade 36a inside, and a suction bell 37 connected below the discharge bowl 36 to form a suction port 37a into the water flow pump casing 31. I have.

The pump casing 31 is fixed to the second floor 2B by the pump base 31a. Inside the pump casing 31, a pump rotating shaft 32 extends along the central axis of the suspended casing 34, and an impeller 38 is provided below the guide vanes 36a. Further, on the downstream side of the discharge elbow 35, a discharge pipe 39 forming a water flow discharge port (not shown) is connected in the horizontal direction. The suction port 37a of the suction bell 37 is submerged in the suction water tank 6.

The pump rotating shaft 32 is rotatably supported by submersible bearings 40 and 41, an intermediate bearing 42, and an outer bearing 43. The submersible bearing 40 supports the lower end of the pump rotating shaft 32 inside the suction bell 37. The submersible bearing 41 supports the lower part of the pump rotating shaft 32 inside the discharge bowl 36. The intermediate bearing 42 supports the intermediate portion of the pump rotating shaft 32 inside the suspended casing 34.

The submersible bearings 40 and 41 and the intermediate bearing 42 are slide bearings that slide into contact with the pump rotating shaft 32. The outer bearing 43 is provided above the discharge elbow 35 and supports the upper portion of the pump rotating shaft 32. The outer bearing 43 is a thrust bearing that receives the thrust load of the pump rotating shaft 32. That is, the thrust load of the pump rotating shaft 32 is received by the pump casing 31 side via the outer bearing 43.

In the pump equipment 1 having the above configuration, when the operation of the drive unit 10 is started, the pump rotation shaft 32 and the impeller 38 rotate via the reduction gear 20. As a result, the liquid in the suction water tank 6 is sucked into the pump casing 31 from the suction port 37a, is pumped vertically upward in the pump casing 31, then bends horizontally and passes through the discharge pipe 39, and is discharged (not shown). It is discharged to the water tank.

As shown in FIG. 1, the speed reducer 20 is supported by the support pedestal 51 and is supported by a plurality of vibration isolation devices 60 via the support pedestal 51. The vibration isolation system 50 including the support stand 51 and the plurality of vibration isolation devices 60 is installed on the first floor 2A of the building foundation 2. On the first floor 2A, an edge foundation 3 that surrounds the installation area of the vibration isolation system 50 (vibration isolation device 60) in a plan view is erected. Inside the edge foundation 3, a step 4 lower than the floor surface of the first floor 2A is formed.

On the step 4, a bulky upper portion 5 for arranging the vibration isolation system 50 (vibration isolation device 60) at a height of the edge foundation 3 or higher is installed. The bulky portion 5 is composed of, for example, a concrete block body similar to the building foundation 2. As a result, the vibration isolation system 50 (vibration isolation device 60) is not hidden under the edge foundation 3, and the adjustment work (described later) of the vibration isolation device 60 becomes easy. Since the position of the speed reducer 20 is higher, a stepping stone or the like may be installed.

FIG. 2 is a plan view of the vibration isolation system 50 according to the first embodiment.
As shown in FIG. 2, the vibration isolation system 50 includes a support pedestal 51 that supports the speed reducer 20, and a plurality of vibration isolation devices 60 that support the support pedestal 51. The support pedestal 51 includes a well girder structure 52 and a top plate 53 fixed to the well girder structure 52 and supporting the speed reducer 20.

The well girder structure 52 is composed of a total of four beam members, two in each of the vertical and horizontal directions in a plan view, and includes overhanging portions 52a to 52h at eight peripheral locations. The anti-vibration devices 60 are provided in the same number as the overhanging portions 52a to 52h, and support each of the overhanging portions 52a to 52h. The plurality of anti-vibration devices 60 are composed of a first anti-vibration device 60A including both an elastic support portion 70 and a sliding support portion 80, which will be described later.

FIG. 3 is a cross-sectional configuration diagram of the anti-vibration device 60 (first anti-vibration device 60A) according to the first embodiment.
As shown in FIG. 3, the anti-vibration device 60 includes a vibration-proof pedestal 61 that receives a load from the speed reducer 20 via a support pedestal 51, an elastic support portion 70 that supports the vibration-proof pedestal 61, and a vibration-proof pedestal 61. It is provided with a sliding support portion 80 that supports and limits the amount of vertical deflection of the elastic support portion 70 to a certain amount, and is capable of skidding according to the lateral vibration of the vibration isolation frame 61.

The anti-vibration stand 61 is a horizontal plate on which the well girder structure 52 is placed. The anti-vibration pedestal 61 is connected to the sole plate 64 (base) via the elastic support portion 70 and the sliding support portion 80. The sole plate 64 is fixed to the building foundation 2 (bulk upper portion 5 in this embodiment) via anchor bolts 65. The vibration isolator 60 includes a pitch stopper 62 and a roll stopper 63 of the vibration isolation frame 61.

The pitch stopper 62 includes a rod 62a that stands vertically (vertically) from the sole plate 64. The rod 62a penetrates the anti-vibration stand 61 in the vertical direction. An upper limit stopper 62b and a lower limit stopper 62c are fixed to the rod 62a. The upper limit stopper 62b is arranged above the anti-vibration stand 61. The lower limit stopper 62c is arranged below the anti-vibration stand 61.

The upper limit stopper 62b and the lower limit stopper 62c are arranged with a gap larger than the thickness of the anti-vibration stand 61. The upper limit stopper 62b and the lower limit stopper 62c set the allowable swing width in the vertical direction of the vibration isolation frame 61. That is, a gap is formed between the upper limit stopper 62b and the anti-vibration gantry 61, and at least one of the lower limit stopper 62c and the anti-vibration gantry 61.

The roll stopper 63 includes a side wall member 63a that stands upright from the sole plate 64. The side wall member 63a supports a horizontal stopper 63b facing the side surface of the anti-vibration pedestal 61. The horizontal stopper 63b sets an allowable swing width in the lateral direction of the anti-vibration stand 61. Reference numeral 63c may be an elastic material. Further, reference numeral 63c may be a sensor that detects contact between the anti-vibration stand 61 and the horizontal stopper 63b. Further, a gap may be formed between the reference numeral 63c and the anti-vibration stand 61.

The elastic support portion 70 is arranged between the anti-vibration pedestal 61 and the sole plate 64, and elastically supports the anti-vibration pedestal 61. The elastic support portions 70 are arranged in pairs with the sliding support portion 80, which will be described later, interposed therebetween. The number of elastic support portions 70 is not limited as long as they can support the anti-vibration pedestal 61 in a well-balanced manner. The elastic support portion 70 includes an elastic material 71 (vibration-proof material) and a plate 72 fixed to the upper surface of the elastic material 71.

As the elastic material 71, a material having a vibration absorbing property such as rubber is used. The material of the elastic material 71 may be selected based on the size of the rotating machine to be supported, the vibration characteristics, and the like. The plate 72 is fixed so as not to come into contact with and separate from the deflection amount adjusting portion 91 described later. That is, the elastic support portion 70 elastically supports the anti-vibration pedestal 61 via the elastic material 71, the plate 72, and the deflection amount adjusting portion 91.

Below the elastic support portion 70, a measurement unit 100 that measures at least one of the load and the vibration applied to the elastic support portion 70 is arranged. The measuring unit 100 is preferably a load cell (three-axis orthogonal measurement type), for example. The measurement result of the measurement unit 100 is output to the detection unit 101. The detection unit 101 detects an abnormality of the speed reducer 20 or a sign of an abnormality based on the measurement result of the measurement unit 100 (described later). The detection unit 101 is composed of an arithmetic unit including a CPU and the like.

The deflection amount adjusting unit 91 adjusts the initial amount of deflection of the elastic support portion 70 in the vertical direction. The deflection amount adjusting unit 91 is composed of a bolt and a nut. The deflection amount adjusting portion 91 is provided on the vibration-proof pedestal 61 side, and by adjusting the amount of protrusion downward from the lower surface of the vibration-proof pedestal 61, the initial deflection amount of the elastic support portion 70 (elastic material 71) in the vertical direction. To adjust.

The slip support portion 80 is arranged between the anti-vibration gantry 61 and the sole plate 64, and supports the anti-vibration gantry 61. The sliding support portion 80 is arranged between the pair of elastic support portions 70 described above. The number of the sliding support portions 80 is not limited, and the arrangement of the sliding support portions 80 and the elastic support portions 70 may be reversed. The sliding support portion 80 includes a first member 81, a sliding portion 82, and a second member 83. The first member 81 and the second member 83 are formed of a rigid member that does not elastically deform unlike the elastic member 71.

The first member 81 is fixed to the sole plate 64. The sliding portion 82 is provided on the upper surface of the first member 81. The sliding portion 82 allows the second member 83 to roll (sideslip) with respect to the first member 81. The sliding portion 82 is made of a polytetrafluoroethylene-based low-friction material, a metal thrust washer, or the like. The second member 83 is fixed so as not to come into contact with and separate from the level adjusting portion 92 described later. That is, the sliding support portion 80 slides and supports the anti-vibration pedestal 61 via the first member 81, the sliding portion 82, the second member 83, and the level adjusting portion 92.

The level adjusting unit 92 adjusts the support height of the anti-vibration pedestal 61 in the sliding support unit 80. The level adjusting unit 92 is composed of bolts and nuts. The level adjusting portion 92 is provided on the anti-vibration pedestal 61 side, and by adjusting the amount of protrusion downward from the lower surface of the anti-vibration gantry 61, the support height of the anti-vibration gantry 61 in the sliding support portion 80 is adjusted. do. In the present embodiment, due to the arrangement with the support frame 51 (well girder structure 52), the level adjusting portions 92 are installed at a plurality of places so that the sliding support portion 80 can be pressed in a well-balanced manner. It doesn't matter.

Next, the adjustment method (particularly the adjustment method at the time of installation work) in the vibration isolator 60 having the above configuration will be described with reference to FIGS. 4 and 5.

4 and 5 are explanatory views of an adjustment method of the vibration isolator 60 according to the first embodiment.
When adjusting the vibration isolator 60, first, as shown in FIG. 4, the elastic support portion 70 is not loaded from the deflection amount adjusting portion 91 (first step). That is, in this state, the anti-vibration pedestal 61 is supported only by the sliding support portion 80.
Next, the level adjusting unit 92 adjusts the support height of the anti-vibration pedestal 61 in the sliding support unit 80 (second step). In this state, the gap between the anti-vibration pedestal 61 and the elastic support portion 70 is the initial gap d.

Next, as shown in FIG. 5, the deflection amount adjusting portion 91 adjusts the initial deflection amount of the elastic support portion 70 in the vertical direction (third step). Specifically, the deflection amount adjusting unit 91 is screwed in, a load is applied to the elastic material 71, and the deflection amount of the elastic material 71 is adjusted. By adjusting the amount of deflection of the elastic material 71, the natural frequency of the elastic material 71 can be adjusted according to the vibration characteristics of the speed reducer 20, and the vibration isolation performance can be optimized.

By the above adjustment, the gap between the anti-vibration pedestal 61 and the elastic support portion 70 has a dimension obtained by adding the initial deflection amount x to the initial gap d.
Finally, in the sliding support portion 80, it is confirmed that the second member 83 (sliding material) is in contact with the sliding portion 82 (sliding material) (supported state).
With the above, the adjustment of the vibration isolator 60 is completed.

Next, the operating principle of the vibration isolator 60 having the above configuration will be described with reference to FIG.

FIG. 6 is an explanatory diagram of the operating principle of the vibration isolator 60 according to the first embodiment.
First, the relationship between the amount of deflection of the elastic material 71 and the natural frequency will be described. As shown in FIG. 6, the load received by the vibration isolator 61 is W, the load (reaction force) related to the elastic material 71 is M, the spring constant (vertical direction) of the elastic material 71 is k, and the amount of deflection of the elastic material 71 (deflection amount). When x is the vertical direction), F, which is the load applied to the sliding support portion 80, is represented by the following equation (1).
F = W-2 ・ M… (1)

Next, since the condition that the sliding portion 82 is in contact is F> 0, the relationships of the following equations (2) and (3) are established.
F = W-2 ・ M> 0… (2)
M <W / 2 ... (3)

Next, since the anti-vibration design conditions are M> 0 and M = k · x, the relationships of the following equations (4) to (6) are established.
0 <M <W / 2 ... (4)
0 <k · x <W / 2… (5)
0 <x <W / 2k ... (6)

Here, the natural frequency f ₀ of the elastic material 71 is represented by the following equation (7). Note that k _d is the dynamic spring constant of the elastic material 71. As shown by the following equation (7), the natural frequency f ₀ can be adjusted by x, which is the amount of deflection of the elastic material 71.

Next, the sliding conditions of the sliding portion 82 will be described. As described above, F, which is the load applied to the sliding support portion 80, is represented by the following equation (8).
F = W-2 ・ k ・ x… (8)

Next, when the frictional force of _{the sliding portion 82 is F 0} and the friction coefficient of the sliding portion 82 is μ ₀ , the relationships of the following equations (9) and (10) are established.
F ₀ = μ ₀ F… (9)
F ₀ = μ ₀ (W-2 ・ k ・ x)… (10)

Next, assuming that the horizontal vibration force received by the vibration isolation frame 61 is P, the condition of the vibration force that the sliding portion 82 slides is PF ₀ > 0. Therefore, the following equation (11), The relationship (12) holds.
P> F ₀ ... (11)
P> μ ₀ (W-2 ・ k ・ x)… (12)

Here, since x> 0, under the _{condition that P> μ 0} · W, it is a condition of slipping regardless of the value of x. On the other hand _{, under the condition that P ≦ μ 0} · W, it becomes a slip condition when the relations of the following equations (13) and (14) are established. That is, x may be adjusted so as to satisfy the following equations (13) and (14).
2μ ₀・ k ・ x> μ ₀・ WP… (13)

Next, the determination of the presence or absence of an abnormality by the detection unit 101 of the vibration isolation device 60 having the above configuration will be described with reference to FIG. 7.

FIG. 7 is a graph showing an example of the measurement result of the measurement unit 100 according to the first embodiment. In FIG. 7, the vertical axis represents the detection level (% with respect to the threshold value), and the horizontal axis represents the date. The threshold value (100%) is indicated by a dotted line.
As shown in FIG. 7, the speed reducer 20 (pump equipment 1) repeatedly starts and stops. The first peak P1 of the detection level on the 13th day is that an earthquake occurred during the stoppage. Since the first peak P1 is equal to or less than the threshold value, the detection unit 101 determines that the sound is sound.

The second peak P2 of the detection level on the 20th day is an earthquake that occurred during operation. Since the second peak P2 exceeded the threshold value, the detection unit 101 determined that there was a possibility of equipment damage (determination of abnormality), and notified an alarm or a request for manufacturer inspection. In this way, by being able to monitor changes in load and vibration during operation, it is possible to grasp how much room there is for abnormal values, and by managing the tendency of the amount of change, it is possible to manage the tendency. It is also possible to predict to some extent the period until abnormal vibration is reached (failure).

According to the vibration isolator 60 having the above configuration, as shown in FIG. 3, by installing the sliding support portion 80 together with the elastic support portion 70, it is possible to prevent the elastic material 71 from being deformed due to vertical sagging. can. As a result, it is possible to eliminate the additional work (initial sagging removal of the elastic material 71, centering work by shim adjustment) peculiar to the anti-vibration stand 61, which has been generated in the past, and it is possible to improve workability and shorten the work process. .. Further, it is possible to prevent the speed reducer 20 from being misaligned due to aging (sagging) of the elastic material 71. Further, in the case of a rotary machine having a large deviation of the center of gravity such as a speed reducer with a fluid coupling, it is difficult to obtain the horizontality of the support pedestal 51, but the sliding support portion 80 improves the construction.

Therefore, according to the above-described embodiment, the vibration-proof pedestal 61 that receives the load from the speed reducer 20, the elastic support portion 70 that supports the vibration-proof pedestal 61, and the elastic support portion 70 that supports the vibration-proof pedestal 61. The anti-vibration device 60 is prevented by adopting a configuration in which the amount of deflection in the vertical direction is limited to a certain amount and a sliding support portion 80 that can slide sideways according to the lateral vibration of the anti-vibration pedestal 61 is provided. While ensuring the vibration performance, it is possible to prevent the elastic support portion 70 from being deformed and the speed reducer 20 from being misaligned due to the sagging of the elastic material 71.

The speed reducer 20 illustrated in the present embodiment is an orthogonal speed reducer, and is subjected to a thrust load on the pump assembly 30 side, and the thrust load (vibration force in the vertical direction) does not act on the speed reducer 20. The excitation force of the machine only needs to be considered in the horizontal direction. Therefore, as shown in the operating principle of the vibration isolator 60 (see FIG. 6), the elastic material 71 is deformed due to the vertical sagging and the core of the speed reducer 20 while ensuring the vibration isolation performance in the horizontal direction. It is possible to prevent deviation.

Further, in the present embodiment, as shown in FIG. 3, since the sliding support portion 80 includes the level adjusting portion 92 for adjusting the support height of the vibration isolation frame 61, the centering work of the speed reducer 20 is easy. It becomes. This makes it possible to improve the workability of the centering work when the speed reducer 20 is newly installed and the recentering work by exchanging the sliding portion 82 and the elastic material 71.

Further, in the present embodiment, since the deflection amount adjusting unit 91 for adjusting the initial deflection amount in the vertical direction of the elastic support portion 70 is provided, the natural frequency of the elastic material 71 is adjusted according to the vibration characteristics of the rotating machine. It is possible to optimize the vibration isolation performance.

Further, in the present embodiment, since the measuring unit 100 for measuring at least one of the load and the vibration applied to the elastic support unit 70 is provided, it is possible to monitor the load and the vibration change during operation. .. Further, by confirming the load amount at the time of construction, the natural frequency of the elastic material 71 can be adjusted more strictly.

Further, in the present embodiment, since the detection unit 101 for detecting the abnormality of the speed reducer 20 or the sign of the abnormality based on the measurement result of the measurement unit 100 is provided, the target device is subjected to the load and vibration change during operation. Abnormality can be detected, it is possible to grasp how much margin there is for the abnormal value, and by managing the tendency of the amount of change, the period until abnormal vibration is reached (failure) can be predicted to some extent. It is also possible to do.

Further, the pump equipment 1 according to the present embodiment includes the vibration isolator 60 (vibration isolation system 50) described above, the speed reducer 20 supported by the vibration isolation device 60, and the pump assembly 30 connected to the speed reducer 20. Therefore, it is possible to prevent deformation of the elastic support portion 70 due to sagging of the elastic material 71 and misalignment of the speed reducer 20 while ensuring anti-vibration performance, and it is possible to ensure the soundness of the pump equipment 1. ..

Further, in the present embodiment, as shown in FIG. 1, the edge foundation 3 surrounding the installation area of the vibration isolation device 60 (vibration isolation system 50) and the vibration isolation device 60 are arranged at a height equal to or higher than the edge foundation 3. Since the bulky portion 5 is provided, the vibration isolator 60 can be installed above the floor level of the first floor 2A without dropping the support stand 51, and the vibration isolator 60 can be installed. Maintenance and maintainability such as replacement of the elastic material 71 are improved.

Further, as shown in FIG. 2, the anti-vibration system 50 of the present embodiment includes a support pedestal 51 for supporting the speed reducer 20 and a plurality of anti-vibration devices 60 for supporting the support pedestal 51, and a plurality of anti-vibration devices are provided. Each device of the vibration device 60 is composed of a first vibration isolation device 60A including both an elastic support portion 70 and a slide support portion 80. According to this configuration, all of the anti-vibration devices 60 have anti-vibration and slip support, and the amount of deflection can be adjusted, so that the anti-vibration performance is extremely high.

The first vibration isolator 60A according to the first embodiment described above may adopt the following modified examples. In the following description, the same or equivalent configurations as those in the above-described embodiment are designated by the same reference numerals, and the description thereof will be simplified or omitted.

FIG. 8 is a cross-sectional configuration diagram showing a modified example of the vibration isolator 60 (first vibration isolator 60A) according to the first embodiment.
In the modified example shown in FIG. 8, a rolling element is used for the sliding portion 82. According to this modification, since the sliding portion 82 has a rolling structure, the friction in the horizontal direction is reduced, and the vibration transmitted to the first member 81 can be reduced. In addition, the influence of wear is less than that of a sliding material such as polytetrafluoroethylene.

FIG. 9 is a cross-sectional configuration diagram showing a modified example of the vibration isolator 60 (first vibration isolator 60A) according to the first embodiment.
In the modified example shown in FIG. 9, the elastic support portion 70 is arranged in the horizontal direction. According to this modification, since all the loads in the vertical direction are handled by the sliding support portion 80, there is no load distribution with the elastic support portion 70. Therefore, there is almost no influence (misalignment) due to the sagging of the elastic material 71. Further, the structure can be simplified by using the elastic support portion 70 in combination with the roll stopper 63 described above.

FIG. 10 is a cross-sectional configuration diagram showing a modified example of the vibration isolator 60 (first vibration isolator 60A) according to the first embodiment.
In the modified example shown in FIG. 10, the level adjusting portion 92 is incorporated as a part of the sliding support portion 80 and arranged under the sliding portion 82. Also in this modification, the performance is the same as that of the basic embodiment (see FIG. 3) of the first embodiment described above.

FIG. 11 is a cross-sectional configuration diagram showing a modified example of the vibration isolator 60 (first vibration isolator 60A) according to the first embodiment.
In the modified example shown in FIG. 11, the level adjusting unit 92 also functions as the deflection amount adjusting unit 91. According to this modification, since it is necessary to adjust the level and the amount of deflection at the same time, the workability is lowered as compared with the basic embodiment of the first embodiment described above. However, since the level adjustment and the deflection amount adjustment are combined, the structure can be simplified.

FIG. 12 is a cross-sectional configuration diagram showing a modified example of the vibration isolator 60 (first vibration isolator 60A) according to the first embodiment.
The modified example shown in FIG. 12 is another example in which the level adjusting unit 92 also functions as the deflection amount adjusting unit 91. In this modification, as in FIG. 10, the level adjusting portion 92 is incorporated as a part of the sliding support portion 80. Also in this modification, since it is necessary to adjust the level and the amount of deflection at the same time, the workability is lower than that of the basic embodiment of the first embodiment described above. However, since the level adjustment and the deflection amount adjustment are combined, the structure can be simplified.

FIG. 13 is a cross-sectional configuration diagram showing a modified example of the vibration isolator 60 (first vibration isolator 60A) according to the first embodiment.
In the modified example shown in FIG. 13, the level adjusting unit 92 is omitted. According to this modification, the level adjustment needs to be adjusted under the sole plate 64 or on the speed reducer 20 side, and the workability is lowered as compared with the basic embodiment of the first embodiment described above. However, since the level adjusting unit 92 is omitted, the structure can be simplified.

FIG. 14 is a cross-sectional configuration diagram showing a modified example of the vibration isolator 60 (first vibration isolator 60A) according to the first embodiment.
The modified example shown in FIG. 14 is another example in which the level adjusting unit 92 is omitted. In this modification, the deflection amount adjusting portion 91 is incorporated as a part of the elastic support portion 70 and is arranged under the elastic material 71. According to this modification, as in FIG. 13, the level adjustment needs to be adjusted under the sole plate 64 or on the speed reducer 20 side, and the workability is lowered as compared with the basic embodiment of the first embodiment described above. .. However, since the level adjusting unit 92 is omitted, the structure can be simplified.

FIG. 15 is a cross-sectional configuration diagram showing a modified example of the vibration isolator 60 (first vibration isolator 60A) according to the first embodiment.
In the modified example shown in FIG. 15, the deflection amount adjusting unit 91 and the level adjusting unit 92 are omitted. According to this modification, the amount of deflection of the elastic material 71 is affected by the manufacturing accuracy and assembly accuracy of parts such as the sliding support portion 80. Further, since the deflection amount adjusting unit 91 is not provided, the vibration isolation performance (natural frequency) cannot be adjusted. However, since the deflection amount adjusting unit 91 and the level adjusting unit 92 are omitted, the structure can be simplified.

FIG. 16 is a cross-sectional configuration diagram showing a modified example of the vibration isolator 60 (first vibration isolator 60A) according to the first embodiment.
In the modified example shown in FIG. 16, the measuring unit 100 is installed between the elastic support unit 70 and the vibration isolation frame 61 (deflection amount adjusting unit 91). According to this modification, the measuring unit 100 is arranged closer to the speed reducer 20 side, and it is possible to more easily confirm the state change of the device.

FIG. 17 is a cross-sectional configuration diagram showing a modified example of the vibration isolator 60 (first vibration isolator 60A) according to the first embodiment.
In the modified example shown in FIG. 17, the measuring unit 100 is installed below the sliding support unit 80. If the measuring unit 100 has a small displacement amount, the measuring unit 100 can be installed below the sliding support unit 80 in this way.

FIG. 18 is a cross-sectional configuration diagram showing a modified example of the vibration isolator 60 (first vibration isolator 60A) according to the first embodiment.
In the modified example shown in FIG. 18, the measuring unit 100 is composed of an acceleration sensor instead of a load cell. When the measuring unit 100 is an acceleration sensor, it is not necessary to sandwich it between the elastic support unit 70 and the sole plate 64, and it may be installed at an arbitrary position on the sole plate 64. Further, by providing the first measuring unit 100a on the upper anti-vibration stand 61 and the second measuring unit 100b on the lower sole plate 64, vibrations on the speed reducer 20 side and the building foundation 2 side of the anti-vibration device 60 are provided. The anti-vibration performance can be confirmed from. Further, the acceleration sensor may be installed on a component connected to the support frame 51 and the sole plate 64.

(Second Embodiment)
Next, a second embodiment of the present invention will be described. In the following description, the same or equivalent configurations as those in the above-described embodiment are designated by the same reference numerals, and the description thereof will be simplified or omitted.

FIG. 19 is a plan view of the vibration isolation system 50 according to the second embodiment.
As shown in FIG. 19, in the vibration isolation system 50 of the second embodiment, the plurality of vibration isolation devices 60 are the first vibration isolation device 60A including both the elastic support portion 70 and the slip support portion 80, and the elastic support portion. Of the 70 and the sliding support portion 80, the second anti-vibration device 60B including only the elastic support portion 70 is configured.

FIG. 20 is a cross-sectional configuration diagram of the vibration isolator 60 (second vibration isolator 60B) according to the second embodiment.
As shown in FIG. 20, the second anti-vibration device 60B includes only the elastic support portion 70 among the elastic support portion 70 and the slide support portion 80. That is, the second anti-vibration device 60B does not include the slip support portion 80 and the level adjusting portion 92 described above.

Returning to FIG. 19, the arrangement of the first vibration isolator 60A and the second vibration isolator 60B will be described. In the overhanging portions 52a to 52h of the support pedestal 51 arranged clockwise from the drive shaft 11 in a plan view, the overhanging portions 52a , 52d, 52e, 52h are supported by the first anti-vibration device 60A, and the overhanging portions 52b, 52c, 52f, 52g are supported by the second anti-vibration device 60B. The arrangement of the first anti-vibration device 60A and the second anti-vibration device 60B in a plan view is a line-symmetrical arrangement with the virtual line passing through the drive shaft 11 as the center line.

According to the second embodiment of the above configuration, since there is no slip support portion 80 in the second vibration isolation device 60B and level adjustment is not required, the number of adjustment portions of the entire vibration isolation system 50 is reduced, and the workability of the adjustment work is improved. improves. The sagging of the elastic material 71 in the second anti-vibration device 60B can be prevented by the slip support portion 80 of the adjacent first anti-vibration device 60A.

(Third Embodiment)
Next, a third embodiment of the present invention will be described. In the following description, the same or equivalent configurations as those in the above-described embodiment are designated by the same reference numerals, and the description thereof will be simplified or omitted.

FIG. 21 is a plan view of the vibration isolation system 50 according to the third embodiment.
As shown in FIG. 21, in the vibration isolation system 50 of the third embodiment, the plurality of vibration isolation devices 60 are the first vibration isolation device 60A including both the elastic support portion 70 and the slip support portion 80, and the elastic support portion. A second anti-vibration device 60B having only the elastic support 70 among the 70 and the slip support 80, and a third anti-vibration device having only the slip support 80 among the elastic support 70 and the slip support 80. It is composed of 60C.

FIG. 22 is a cross-sectional configuration diagram of the vibration isolator 60 (third vibration isolator 60C) according to the third embodiment.
As shown in FIG. 22, the third anti-vibration device 60C includes only the slip support portion 80 among the elastic support portion 70 and the slide support portion 80. That is, the third vibration isolator 60C does not include the elastic support portion 70 and the deflection amount adjusting portion 91 described above.

Returning to FIG. 21, the arrangement of the first anti-vibration device 60A, the second anti-vibration device 60B, and the third anti-vibration device 60C will be described. In ~ 52h, the overhanging portions 52a, 52d, 52e, 52h are supported by the first anti-vibration device 60A, the overhanging portions 52b, 52g are supported by the second anti-vibration device 60B, and the overhanging portions 52c, 52f are supported by the third anti-vibration device. It is supported by the device 60C. The arrangement of the first anti-vibration device 60A, the second anti-vibration device 60B, and the third anti-vibration device 60C in a plan view is a line-symmetrical arrangement centered on a virtual line passing through the drive shaft 11.

According to the third embodiment of the above configuration, the second anti-vibration device 60B has no slip support portion 80 and level adjustment becomes unnecessary, and the third anti-vibration device 60C has no elastic support portion 70 and the amount of deflection. Since adjustment is not required, the number of adjustment parts of the entire vibration isolation system 50 is reduced, and the workability of the adjustment work is improved. The sagging of the elastic material 71 in the second anti-vibration device 60B can be prevented by the slip support portion 80 of the adjacent first anti-vibration device 60A to the third anti-vibration device 60C.

Although preferred embodiments of the present invention have been described and described above, it should be understood that these are exemplary and should not be considered as limiting. Additions, omissions, substitutions, and other modifications can be made without departing from the scope of the invention. Therefore, the present invention should not be considered limited by the above description, but is limited by the claims.

For example, in the above embodiment, as shown in FIG. 1, a vertical shaft pump is illustrated as the pump assembly 30, but the screw pump has an inclined rotating shaft as disclosed in Japanese Patent Application Laid-Open No. 2011-21586. It doesn't matter. For example, the vibration isolator 60 (vibration isolation system 50) described above can be applied to the portion indicated by reference numeral 16 of JP2011-21586A. In this case, the anti-vibration device 60 is arranged so as to be inclined, but the sliding support portion 80 may be slidable in this inclined state. That is, the "lateral shake" referred to in the present application includes not only the horizontal roll with the horizontal plane as 0 ° but also the roll in the tilted state within the range of ± 30 °.

Further, for example, in the above embodiment, as shown in FIG. 2, the configuration in which the support pedestal 51 includes the well girder structure 52 has been illustrated, but the support pedestal 51 may have a configuration in which the double girder structure is provided. That is, the number of vibration isolators 60 is not limited to eight, and may be four.

Further, for example, in the above embodiment, as shown in FIG. 1, the pump equipment 1 arranges the vibration isolator 60 at a height of the edge foundation 3 surrounding the installation area of the vibration isolator 60 and the edge foundation 3 or higher. Although the configuration including the bulky portion 5 is illustrated, the configuration including the building foundation 2 without the edge foundation 3 may be used. In this case, a steel cover or the like may be installed on the step 4 so that it can be removed during maintenance work or the like.

Further, for example, in the above embodiment, the configuration in which the vibration isolator 60 (vibration isolation system 50) supports the speed reducer 20 has been illustrated, but a configuration in which the drive unit 10 is supported may be used. Further, the vibration isolator 60 is not limited to the speed reducer 20 and the drive unit 10, and can be applied to vibration isolation of all rotating machines.

1 Pump equipment 2 Building foundation (foundation)
3 Edge foundation 5 Bulked upper part 20 Reducer (rotary machine)
30 Pump assembly 50 Anti-vibration system 51 Support stand 60 Anti-vibration device 60A 1st anti-vibration device 60B 2nd anti-vibration device 60C 3rd anti-vibration device 61 Anti-vibration stand 70 Elastic support part 80 Support part 91 Deflection amount adjusting part 92 Level adjustment unit 100 Measurement unit 101 Detection unit

Claims (9)

A vibration-proof stand that receives a load from a rotating machine,
An elastic support portion that supports the anti-vibration stand and
The anti-vibration gantry is supported, the amount of vertical deflection of the elastic support portion is limited to a certain amount, and the anti-vibration gantry is provided with a sliding support portion that can skid according to the lateral vibration of the anti-vibration pedestal. A characteristic anti-vibration device for rotating machines. The anti-vibration device for a rotating machine according to claim 1, further comprising a level adjusting portion for adjusting the support height of the anti-vibration pedestal in the sliding support portion. The anti-vibration device for a rotating machine according to claim 1 or 2, further comprising a deflection amount adjusting portion for adjusting the initial deflection amount in the vertical direction of the elastic support portion. Claims 1 to 1, further comprising a measuring unit for measuring at least one of a load and a vibration applied to at least one of the anti-vibration stand, the elastic support portion, and the sliding support portion. The anti-vibration device for a rotating machine according to any one of 3. The anti-vibration device for a rotating machine according to claim 4, further comprising a detecting unit that detects an abnormality or a sign of the abnormality of the rotating machine based on the measurement result of the measuring unit. The anti-vibration device according to any one of claims 1 to 5.
The rotating machine supported by the anti-vibration device and
A pump facility comprising a pump assembly connected to the rotary machine. The edge foundation surrounding the installation area of the anti-vibration device and
The pump equipment according to claim 6, further comprising a bulky portion for arranging the vibration isolator at a height equal to or higher than the edge foundation. The pump equipment according to claim 6, further comprising a foundation having no edge foundation surrounding the installation area of the vibration isolator. A vibration-proof stand that receives a load from a rotating machine,
An elastic support portion that supports the anti-vibration stand and
A slip support portion that supports the anti-vibration pedestal, limits the amount of vertical deflection of the elastic support portion to a certain range, and can skid according to the lateral vibration of the anti-vibration pedestal.
A level adjusting unit that adjusts the support height of the anti-vibration stand in the sliding support portion, and a level adjusting unit.
A method for adjusting a vibration isolator of a rotating machine, comprising a deflection amount adjusting portion for adjusting the initial deflection amount in the vertical direction of the elastic support portion.
The first step in which a load is not applied from the deflection amount adjusting portion to the elastic support portion, and
After the first step, a second step of adjusting the support height of the anti-vibration pedestal in the slip support portion by the level adjusting portion, and
A method for adjusting a vibration isolator of a rotating machine, which comprises, after the second step, a third step of adjusting the initial vertical deflection amount of the elastic support portion by the deflection amount adjusting portion.

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