JP2003247495A - Silencing box and fluid machinery - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a silencing box and a fluid machinery, in which noise of a machine, even though it inevitably develops vibration and pulsation, is surely reduced by housing the machine in the inside, and a heat-generating part such as a motor contained in the machine can be positively cooled. <P>SOLUTION: In the silencer, a noise-absorbing material 80 is stuck on the internal surface, and the inside is perfectly cut off from the outside. A gas sucked from a sucking port 84 flows through the inside, which is constituted as a part of a pipe, and the gas is discharged from an outlet 86. <P>COPYRIGHT: (C)2003,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a sound deadening box and a fluid machine, and particularly to a machine such as a roots type positive displacement biaxial fluid machine, which inevitably causes problems of noise and pulsation of discharged fluid due to its structure. Even so, it relates to a silencing box capable of reliably reducing the noise and a fluid machine in which the silencing box is unitized.

[0002]

2. Description of the Related Art For example, a displacement type two-shaft fluid machine which is optimally used as a blower for compressing and transferring gas such as air and combustible gas includes a roots type, a tooth (decad shaped rotor) type,
There are various types such as screw type. Here, for example, a roots-type blower includes a pair of pump rotors (roots rotors) that rotate in synchronization in opposite directions, and the pump rotors are housed in a pump chamber of a pump casing and rotated in synchronization in opposite directions. The gas is sucked into the pump chamber, and the gas enclosed between the rotor and the pump casing is pressurized and sequentially discharged.

In this way, the volume type 2 such as the roots type blower is used.
The axial fluid machine is configured to discharge the gas a plurality of times per one rotation of the pump rotor. Due to its structure,
The problems of noise and pulsation of the ejected fluid are unavoidable.

[0004]

Conventionally, such a positive displacement biaxial fluid machine such as a roots type blower is generally used in a place where noise is not a serious problem.
For example, although a silencer is widely provided at the discharge port, no measures have been taken to reduce overall noise. However, it is expected that such a fluid machine such as a roots blower will be widely used, for example, for household use in the future, and thus, when it is used for household use, noise is not only a serious problem. However, it is considered that there are also dimensional restrictions.

It should be noted that, if it is attempted to improve the manufacturing precision to reduce the noise and vibration generated by the machine itself such as the roots type blower, the manufacturing is considerably difficult, and there is a certain limit in reducing the noise and vibration. .

The present invention has been made in view of the above, and even if a machine inevitably suffers from vibration or pulsation, it is housed inside to surely reduce noise, and is incorporated in such a machine. An object of the present invention is to provide a sound deadening box capable of reliably cooling a heat generating part such as a motor and a fluid machine in which the sound deadening box is integrated.

[0007]

According to a first aspect of the present invention, a sound absorbing material is attached to the inner peripheral surface to completely block the inside and the outside, and the gas sucked from the suction part flows inside and is discharged from the discharge part. It is a sound deadening box characterized by being used as a part of a pipe to be installed. In this way, by attaching a sound absorbing material to the inner peripheral surface and completely blocking the inside and outside, the noise generated by the equipment housed inside the sound deadening box is prevented from leaking to the outside, and the sound deadening box is connected to the piping. By making it a part,
The gas sucked into the inside can surely cool the heating portion such as the motor and the blower body incorporated in the device housed inside.

The invention according to claim 2 is characterized in that it has a support base which is attached via a vibration-proof rubber and arranged inside, and the equipment is supported by this support base. It is a sound deadening box. Thus, the vibration generated by the device is absorbed by the vibration isolating rubber, the vibration is prevented from being transmitted to the vibration isolating box, and the noise can be reduced.

The invention according to claim 3 is the sound deadening box according to claim 1 or 2, wherein a filter is arranged inside. Thus, the filter for filtering the gas sucked into the sound deadening box is not provided outside the sound deadening box, but is integrated into the sound deadening box, and the device can be made compact and compact.

The invention according to claim 4 is the silencer box according to any one of claims 1 to 3, wherein a silencer is provided inside. In this way, by providing the silencer inside the silencer box, it is possible to prevent internal noise from leaking from the suction portion.

According to a fifth aspect of the present invention, in a fluid machine having a motor installed therein, a sound absorbing material is attached to the inner peripheral surface to completely shut off the inside and outside, and the gas sucked from the suction part flows inside to discharge the part. It is a fluid machine characterized in that a fluid machine body having a built-in motor is housed inside a sound deadening box which is a part of a pipe discharged from the machine. The invention according to claim 6 is the fluid machine according to claim 5, wherein the fluid machine body is a positive displacement biaxial fluid machine.

[0012]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, embodiments of the present invention will be described with reference to the drawings. 1 to 5 show a fluid machine including a sound deadening box according to an embodiment of the present invention. This example
It is applied to a roots-type blower of a biaxial fluid machine, and this roots-type blower (fluid machine) has a motor 10 and a pump unit 12, and the motor 10 and the pump unit 12 are integrated via a bracket 14. The blower main body (machine main body) 16 connected to the main body 16 and the muffler box 18 having the blower main body 16 housed therein are mainly configured.

The motor 10 has a motor rotor portion 20 and a motor stator portion 22. An output shaft (spindle) 24 is integrally fixed inside the motor rotor portion 20, and the motor stator portion 22 includes a motor frame 26. It is fixed to the inner surface. The output shaft 24 is positioned on both sides of the motor rotor portion 20 and is rotatably supported via a motor anti-load side bearing 28 housed in the motor frame 26 and a motor load side bearing 30 housed in the bracket 14. As the motor 10 is driven, it rotates integrally with the motor rotor section 20.

In this example, the motor load side bearing 30 is housed in the bracket 14 that connects the motor 10 and the pump portion 12, so that the bracket 14 allows the load side bearing 3 of the motor 10.
The bearing housing for accommodating 0 is also used. With such a configuration, it is not necessary to provide a bearing housing for accommodating the bearing on the load side of the motor 10, the number of parts and the number of working steps are reduced, and a fluid machine corresponding to the thickness of the bearing housing is provided. The total length of can be shortened.

The pump portion 12 has a pump casing 32 that defines a pump chamber 32a therein and a pump cover 34 that closes an opening of the pump casing 32. Inside the pump chamber 32a, a pair of pump rotors is provided. (Roots rotors) 36 and 38 are housed at positions facing each other. Here, the pump casing 32 and the pump rotors 36 and 38 are disposed between the outer peripheral edges of the pump rotors 36 and 38 and the inner wall of the pump casing 32, and the pump rotor 3.
6 and 38 are formed in such a shape that a slight clearance is formed between them and are arranged at predetermined positions. The pump casing 32 includes a pair of pump rotors 36, 38.
And a suction port 32b and a discharge port 32c are provided at positions laterally opposite to each other.

In this example, as the pump rotors 36 and 38, a three-leaf type having a three-leaf shape is used, and when the pump rotors 36 and 38 rotate synchronously in the opposite directions, gas is introduced from the suction port 32b into the pump chamber. 32a is sucked into the inside of the pump 32a, and the sucked gas is trapped between the pump rotors 36 and 38 and the pump casing 32, transferred to the discharge side, and discharged sequentially from the discharge port 32c. In the three-lobed pump rotors 36 and 38, one pump rotor has three troughs, and therefore the pump is exhausted six times per revolution. It is needless to say that the pump rotor may be a cocoon-shaped two-leaf type, four-leaf type or more, and further, multi-leaf type of 10 or more leaves. By increasing the number of leaves of the pump rotor in this way, the pulsation of the discharged fluid can be reduced and the pump efficiency can be improved.

The pump rotors 36, 38 are cantilevered by being connected to the free ends of rotating shafts 40, 42 arranged in parallel with each other. Here, one rotating shaft 40 serves as a drive shaft, and the other rotating shaft 42 serves as a driven shaft. That is, the drive shaft (rotating shaft) 40
One end of is connected to the output shaft 24 of the motor 10 via the coupling 44, and the drive-side pump rotor 36 is connected to the opened other end. On the other hand, driven shaft (rotating shaft) 4
2 is open at both ends, and the driven pump rotor 38 is connected to the open end of the pump casing 32 side. In this way, the pump rotors 36, 38 are cantilevered by connecting to the free ends of the rotary shafts 40, 42 so that the rotary shafts 40, 42 do not project to the opposite motor side of the pump rotors 36, 38. Accordingly, the length along the axial direction can be shortened and the weight can be reduced accordingly.

The coupling 44 is provided at a position as close to the motor rotor portion 20 of the motor 10 as possible, that is, in the wall body which also serves as a bearing housing for accommodating the load side bearing 30 of the motor 10 of the bracket 14 and is provided with the recess 14a. The end of the coupling 44 is arranged in the recess 14a. In this way, by disposing the coupling 44 that connects the drive shaft 40 and the output shaft 24 of the motor 10 in the vicinity of the motor rotor portion 20 of the motor 10, the total length of the fluid machine can be further shortened.

As the coupling 44, in this example, as shown in FIG. 4, a pair of joint pieces 46 and 4 having the same shape.
8 and the elastic body 5 interposed between the joint pieces 46 and 48.
0 is used, and the elastic body shaft coupling in which the torque of one joint piece 46 is transmitted to the other joint piece 48 via the elastic body 50 is used. That is, the pair of joint pieces 46, 48
A plurality of protrusions 46a and 48a which are arranged alternately in parallel to each other. The protrusions 46a of the one joint piece 46 and the protrusions 4 of the other joint piece 48 facing each other are provided.
8a, a plurality of protrusions 50a provided on the outer peripheral portion of the elastic body 50 are respectively located, and the protrusion 4 of one joint piece 46 is located.
The torque is transmitted from 6a to the convex portion 50a of the elastic body 50, and from the convex portion 50a of the elastic body 50 to the protrusion 48a of the other joint piece 48.

As described above, by using the elastic shaft coupling as the coupling 44, the output shaft 24 of the motor 10
Even if there is a deviation (error) between the axis of the shaft and the axis of the drive shaft 40, this deviation is absorbed by the elastic body 50.
The centering work for connecting the drive shaft 40 to the output shaft 24 of the motor 10 can be eliminated. Furthermore, the elastic body 50
The heat insulation of the motor 10 blocks the heat generated from the motor 10 from being transmitted to the pump section 12 side, and the thermal expansion of the pump casing 32 and the pump rotors 36, 38 of the pump section 12 and the temperature rise of the handled gas. It is possible to prevent a decrease in pump efficiency due to a decrease in gas density due to. In particular, the pump casing 32 and the pump rotors 36 and 38 are susceptible to thermal expansion because the clearance between them is extremely small, and in a gas machine, when the gas temperature rises, the gas density decreases and the efficiency is reduced. This adiabatic effect is extremely important because it causes a decrease.

A pair of timing gears 5 meshing with each other is provided at predetermined positions along the lengthwise direction of the rotary shafts 40 and 42.
2, 54 are fixed. As a result, the drive shaft (rotary shaft) 40 and the driven shaft (rotary shaft) 42 are rotated in synchronization in opposite directions via the timing gears 52 and 54. By using a two-axis synchronous motor to rotate the pair of rotary shafts in synchronization in opposite directions, it is possible to eliminate the need to use a timing gear.

Here, in this example, the timing gears 52 and 54 can be fixed to arbitrary positions of the rotary shafts 40 and 42. This will be described with reference to FIG. Although FIG. 5 shows an example in which the timing gear 52 is fixed to the drive shaft 40, the same applies to the driven shaft 42.

That is, a hollow truncated cone-shaped collet 56 having a slit 56a and an outer peripheral surface having a tapered surface 56b,
The stopper 58 has a hollow portion whose inner peripheral surface is an inverse tapered surface 58a facing the tapered surface 56b of the collet 56. Then, with the collet 56 accommodated in the hollow portion of the stopper 58, the drive shaft 40 is inserted into the stopper 58 and the timing gear 52, and the stopper 58 is inserted.
With the timing gear 52 positioned at a predetermined position along the axial direction of the drive shaft 40, the bolt 60 is inserted into the hole 58b provided in the stopper 58 and tightened. As a result, the stopper 58 and the timing gear 52 are directly fastened via the bolt 60, and as the bolt 60 is fastened, the reverse taper surface 58a of the stopper 58 is secured to the collet 5.
When the collet 56 is advanced in contact with the tapered surface 56b of No. 6, the collet 56 is pressed inward in a wedge shape, the collet 56 is elastically deformed through the slit 56a, and the drive shaft 40 is tightened.

As a result, by tightening the bolt 60, the timing gear 52 and the stopper 58 are connected to each other by the bolt 60.
It is possible to fix the stopper 58 to the drive shaft 40 via the collet 56 that is directly fastened via the collet 56 and elastically deformed by tightening the bolt 60. As a result, the timing gear 52 can be fixed at an arbitrary position along the axial direction of the drive shaft 40, and fine adjustment of the fixing position of the timing gear 52 can be performed easily and accurately. That is, it is possible to make fine adjustments that cannot be achieved by fixing with a conventional general key. Moreover, by providing the tapered surface 56b on the outer peripheral surface of the collet 56 and the reverse tapered surface 58a facing the tapered surface 56b in the hollow portion of the stopper 58, the stopper 58 and the timing gear 5 on the drive shaft 40 are provided.
2 can be fixed more firmly and stably.

The rotary shafts 40 and 42 are connected to the timing gear 5
It is rotatably supported by bearings 62 and 64 on both sides sandwiching 2, 54. Here, the load side bearing 62 is accommodated in the through hole 32d provided in the pump casing 32, and the anti-load side bearing 64 is accommodated in the through hole 66a provided in the box portion 66 integrally connected to the pump casing 32. Has been done. That is, the timing gears 52 and 54 are
It is housed in the box portion 66, and is located almost at the center of the blower body 16, so that it can be balanced and contribute to the space reduction.

Further, in order to prevent the grease used as a lubricant for the timing gears 52 and 54 from flowing into the pump chamber 32a, the outer peripheral surfaces of the rotary shafts 40 and 42 and the through hole 32d of the pump casing 32 are formed. A V ring 67 and a seal ring 68 are interposed between the inner peripheral surface and the inner peripheral surface.

As described above, the box portion 66 is integrally connected to the pump casing 32, and the timing gears 52 and 54 are accommodated in the box portion 66, whereby a gear box for accommodating the timing gear is separately provided. It is possible to reduce the number of parts and the number of processing steps as compared with. Moreover, the through hole 32d provided in the pump casing 32
By inserting the pair of rotary shafts 40 and 42 into the through holes 66a provided in the box portion 66 and rotatably supporting them, the through hole 32d of the pump casing 32 and the through hole 66a of the box portion 66 are It is possible to form by so-called concentric processing. As described above, the through hole 32d provided in the pump casing 32 and the through hole 66a provided in the box portion 66 are formed by concentric processing to increase the concentricity. It is possible to prevent the vibrations of the pump rotors 36 and 38 and to perform stable operation.

Further, a C-shaped retaining ring 70 is attached to each end of the rotary shafts 40 and 42 on the side of the motor 10, and the C-shaped retaining rings 70 and the rotary shafts 40 and 42 are rotatably supported. The compression coil springs 72 are respectively interposed between the load side bearings 64. As a result, the rotary shafts 40, 42
Is urged in the axial direction toward the motor 10 side.

In this way, by urging the rotary shafts 40, 42 toward one side (in this example, the motor 10 side) in the axial direction, vibration of the rotary shafts 40, 42 along the axial direction is prevented. You can Moreover, the clearance along the axial direction between the pump casing 32 and the pump rotors 36, 38 can be adjusted during assembly, and this clearance can be kept constant during operation.

The muffling box 18 has a flat base 74.
And a box 76 that surrounds the four sides of the base 74 and surrounds the four sides, and a lid 78 that closes the upper end opening of the box 76.
And have. All the joints of the sound deadening box 18 are joined by welding, and a sound absorbing material 80 such as a sponge is attached to the inner peripheral surface of the sound deadening box 18. Further, an elastic body 8 such as rubber is provided between the box body 76 and the lid body 78.
2 is installed. This completely shuts off the inside and outside of the muffling box 18 so that the sound in the muffling box 18 does not leak outside.

Further, on the side of the muffling box 18,
A suction unit 84 and a discharge unit 86 are provided, and a silencer 88 configured by alternately arranging baffles, for example, is provided inside the muffling box 18. Further, a power cable 89 extends through the side portion of the muffling box 18. Here, the suction part 84 is opened inside the muffling box 18, the silencer 88 and the suction port 32 b of the pump casing 32 are the suction pipe 90, and the discharge port 32 c of the pump casing 32 and the discharge part 86 are the discharge pipe 9.
Two are connected respectively. As a result, the interior of the muffling box 18 constitutes a part of the pipe. The suction part 84 and the discharge part 86 are separated from each other by using a dedicated joint.

That is, when the pump rotors 36 and 38 rotate synchronously in the opposite directions as the motor 10 is driven,
With the rotation of the pump rotors 36, 38, gas such as air is sucked into the muffling box 18 from the suction portion 84. The gas sucked into the muffler box 18 flows into the silencer 88, and the silencer 8
8 flows along the periphery of the motor 10 in the process of flowing into the motor 8 to cool the motor 10, and further from the silencer 88 to the suction pipe 90.
Flow into the pump chamber 32a through the pump rotor 3
6,38, the pressure is increased, and the discharge portion 86 passes through the discharge pipe 92.
It is designed to be discharged from the outside. Here, by providing the silencer 88 in the muffling box 18, it is possible to prevent particularly internal noise from leaking from the suction portion 84.

The blower main body 16 is attached to a support base 94, and the support base 94 is attached to a base 74 of the sound deadening box 18 via a vibration-proof rubber 96. Further, a suction pipe 90 connecting the silencer 88 and the suction port 32b of the pump casing 32, and a discharge port 32 of the pump casing 32.
The discharge pipe 92 connecting the c and the discharge portion 86 is made of, for example, a flexible tube made of resin. As a result, the vibration generated in the blower main body 16 is suppressed by the muffler box 1.
8 to prevent noise, reduce noise and
Work efficiency can be improved.

A characteristic of the roots type blower is that it has large vibration and noise. As described above, the blower body 16 integrally formed is shut off from the inside and outside of the silencer box 18.
It is housed inside to prevent the internal sound from leaking to the outside and also to prevent the vibration generated in the blower body 16 from vibrating.
This vibration and noise can be greatly reduced by preventing the noise from being absorbed by 6 and transmitted to the muffling box 18.

FIG. 6 shows another example of the muffling box 18. This is because the inside of the rectangular box 76 is
0 and 102, a filter housing portion 106 that houses the filter 104 therein, and a pair of baffles 108, for example.
a and 108b are alternately arranged to constitute a silencer 110, and a silencer section 112 and a blower main body accommodating section 114 for accommodating the blower main body 16 (see FIGS. 1 to 3) are divided into partition plates 100 and 102. Gas inlet 100
a and 102a are provided. Then, as shown by the arrow in FIG. 6, the gas such as the air sucked from the suction portion 84 (see FIG. 1) is passed through the filter 104 and the gas intake port 1
00a into the silencer portion 112, and after passing through the silencer 110 of the silencer portion 112 to be silenced, the blower body accommodating portion 114 from the gas intake port 102a.
It is designed to flow in.

According to this example, the filter 104 for filtering the gas sucked into the sound deadening box 18 can be integrated into the sound deadening box 18 without being provided outside the sound deadening box 18, and the sound deadening box 18 can be integrated. By disposing the silencer 110 inside and integrating them, it is possible to reduce the overall size.

[0037]

As described above, according to the present invention,
Even if a machine inevitably vibrates or pulsates, it can be housed inside to reliably reduce noise, and moreover, a heat generating portion such as a motor built into such a machine can be reliably cooled. In addition, by housing the fluid machine inside to form a unit, it is possible to meet the demand for miniaturization of the fluid machine.

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional front view showing a fluid machine (roots type blower) including a sound deadening box according to an embodiment of the present invention.

FIG. 2 is a sectional view taken along the line AA of FIG.

FIG. 3 is a sectional view taken along line BB of FIG.

FIG. 4 is an exploded perspective view showing a coupling.

FIG. 5 is an exploded perspective view showing a fixing portion of the timing gear.

FIG. 6 is a perspective view showing a main part of a sound deadening box according to another embodiment of the present invention.

[Explanation of symbols]

10 motors 12 Pump section 14 bracket 16 Blower body (machine body) 18 silence box 20 Motor rotor part 22 Motor stator 24 Output shaft 28, 30, 62, 64 bearings 32 Pump casing 32a pump room 32b suction port 32c outlet 32d through hole 36,38 Pump rotor 40 rotating shaft (driving shaft) 42 rotating shaft (driven shaft) 44 Coupling 46,48 joint piece 46a, 48a protrusion 50 elastic body 50a convex part 52,54 Timing gear 56 collets 56a slit 56b Tapered surface 58 stopper 58a Reverse taper surface 58b hole 60 volts 66 box section 66a through hole 72 Compression coil spring 74 base 76 box 78 Lid 80 sound absorbing material 82 Elastic body 84 Suction part 86 Discharge part 88,94 silencer 90 Suction tube 92 Discharge pipe 94 Support 96 anti-vibration rubber 100,102 partition boards 104 filters 106 Filter storage 108a, 108b baffle 110 silencer 112 Silencer part 114 Blower body storage

Continued front page    (72) Inventor Yasutaka Konishi             11-1 Haneda Asahi-cho, Ota-ku, Tokyo Co., Ltd.             Inside the EBARA CORPORATION F term (reference) 3G004 AA00 BA01 BA04 BA05 CA13                       CA14 DA15 EA03 EA05 EA06                 3H003 BA07 BB05                 3H029 AA06 AA15 AB02 BB21 CC28

Claims (6)

[Claims] 1. A sound absorbing material is attached to the inner peripheral surface to completely block the inside and the outside, and the gas sucked from the suction part is a part of a pipe which flows through the inside and is discharged from the discharge part. Silence box. 2. The sound deadening box according to claim 1, further comprising a support stand attached inside the vibration proof rubber to support the device. 3. The sound deadening box according to claim 1, wherein a filter is arranged inside. 4. The silencer box according to claim 1, further comprising a silencer provided therein. 5. A fluid machine incorporating a motor, wherein a sound absorbing material is attached to the inner peripheral surface to completely shut off the inside and the outside, and the gas sucked from the suction part flows inside and is discharged from the discharge part. A fluid machine characterized in that a fluid machine body having a built-in motor is housed inside a muffler box which is a section. 6. The fluid machine according to claim 5, wherein the fluid machine body is a positive displacement biaxial fluid machine.