CN207598456U - A kind of duct type active flow pulsation damping device for large reciprocating compressor - Google Patents
A kind of duct type active flow pulsation damping device for large reciprocating compressor Download PDFInfo
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- CN207598456U CN207598456U CN201721730718.1U CN201721730718U CN207598456U CN 207598456 U CN207598456 U CN 207598456U CN 201721730718 U CN201721730718 U CN 201721730718U CN 207598456 U CN207598456 U CN 207598456U
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- pipeline
- return tube
- branch pipeline
- surge tank
- reciprocating compressor
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Abstract
The utility model belongs to compressor field, and disclose a kind of duct type active flow pulsation damping device for large reciprocating compressor, including surge tank pedestal, buffering tank, surge tank admission line, surge tank discharge duct and pipeline group, the pipeline group has more pipelines, they are respectively first branch pipeline, the second branch pipeline, the first return tube and the second return tube；The first branch pipeline and the first return tube link together, to inhibit the pulsation of odd multiple number of frequency；The second branch pipeline and the second return tube link together, to inhibit the pulsation of even number overtones band.The utility model causes the fluid phase difference of two bursts of confluences on the contrary to play the purpose of active suppression pulsation, in addition, pipeline is placed on inside high-pressure buffering pot, the bearing capacity of bypass line can be caused to substantially reduce in this way.On the other hand since duct segments use the controllability of therefore increased pipe range to adapt to different operation of reciprocating compressor rotating speeds.
Description
Technical field
The utility model belongs to compressor field, more particularly, to a kind of duct type for large reciprocating compressor
Active flow pulsation damping device.
Background technology
Reciprocating compressor, for improving the common apparatus of gas pressure and conveying, is widely used in chemical industry, stone as a kind of
The industries such as oil and natural gas, and since reciprocating compressor compression pressure range is wide, it is especially wide in high pressure field application
It is general.Reciprocating compressor is a kind of reciprocating volume compressor, and piston moves back and forth under the drive of crank connecting link, simultaneously
Air valve is turned on and off under the conditions of certain pressure, leads to intermittent suction and discharge, so that there is pressure in suction air pipe
With the cyclic swing of speed, i.e. gas.Excessive gas easily causes pipe vibration, and pipe vibration easily makes pipeline
Attachment, instrument and meter service life substantially reduce, and violent pipe vibration may be such that pipe connection portion position ruptures, and may lead
Cause the safety accidents such as leakage.It is therefore proposed that a kind of effective gas attenuating device is significant.
Common gas damped system has active attenuation and passive attenuation, decays, such as orifice plate the most commonly used is passive,
Helmholtz resonator, vessel buffers etc., these passive type gas attenuating devices are commonly available to a degree of air-flow
Pulsation attenuation.Active attenuation is since the pressure wave of generation is opposite with the pressure wave phase of pipe transmmision therefore can be largely
The pulsation in calculation for pipelines system of compressor is reduced, but usually unadjustable or be difficult in reciprocating compressor pipeline.Such as
106382231 A of CN disclose a kind of active attenuation screw compressor gas device, and hole is processed on exhaust bearing block
Road, to achieve the purpose that active attenuation is pulsed, it is higher to be typically due to screw compressor running speed, while the male rotor number of teeth
Typically larger than reciprocating compressor effect institute value, therefore what screw compressor ripple frequency was generated far above reciprocating compressor
Ripple frequency.Therefore required L is smaller, therefore the device is difficult to use in reciprocating compressor system.In addition the duct once processes
Just it is unadjustable.A kind of pipeline noise reduction system and method are proposed in patent CN106469551A, the system is by obtaining pipeline
Interior sound-source signal passes to controller and generates corresponding inhibition signal according to source of students signal to achieve the purpose that active noise reduction,
The system is difficult to process corresponding signal generation device to be suitable for that can generate the inhibition signal being adapted with original signal
In high-pressure fluid.
Utility model content
For the disadvantages described above or Improvement requirement of the prior art, the utility model provides a kind of for large-scale reciprocating compression
The duct type active flow pulsation damping device of machine can realize reciprocating compressor gas active attenuation and available for high pressure
In working media.
To achieve the above object, according to the utility model, a kind of duct type master for large reciprocating compressor is provided
It takes offence and flows pulsation damping device, which is characterized in that including surge tank pedestal, buffering tank, surge tank admission line, surge tank
Discharge duct and pipeline group, wherein,
The buffering tank is mounted on the surge tank pedestal；
The surge tank admission line and surge tank discharge duct are separately mounted on the buffering tank；
The pipeline group has more pipelines, they are respectively first branch pipeline, the second branch pipeline, the first return tube
With the second return tube, one end of the first branch pipeline and the second branch pipeline passes through four-way connection A and four-way connection B respectively
On the surge tank admission line；
One end of first return tube is mounted on by four-way connection A on the surge tank admission line by described；
One end of second return tube is mounted on by four-way connection B on the surge tank admission line by described；
The first branch pipeline and the connection of the first return tube, the second branch pipeline and the connection of the second return tube.
Preferably, pipe joint device is further included, the pipe joint device has among multiple pipe joints and Duo Gen
Connecting tube, each pipe joint are separately mounted on the buffering tank, and the every intermediate connection tube is connected described in two
Pipe joint, the first branch pipeline and the first return tube are connected by the pipe joint device, the second branch pipe
Line and the second return tube are connected also by the pipe joint device.
Preferably, two two to make up line described in one that make up line and have at least are set in the buffering tank
End is connected on a pipe joint, for connecting the first branch pipeline and the first return tube, also one
The both ends to make up line are connected on a pipe joint, for connecting the second branch pipeline and second
Return tube.
In general, it can obtain down the above technical solutions conceived by the present invention are compared with the prior art,
Row advantageous effect：
The utility model is by propagation law of the pulsation in pipeline so that the fluid phases of two bursts of confluences are on the contrary to play
The purpose of active suppression pulsation, it is the realizability so that the present apparatus at the same time to correspond to high-pressure medium, and pipeline is placed on height
It presses inside surge tank, the bearing capacity of bypass line can be caused to substantially reduce in this way.On the other hand since duct segments use
Therefore the controllability of increased pipe range is to adapt to different operation of reciprocating compressor rotating speeds.
Description of the drawings
Fig. 1 is the structure diagram of the utility model；
Fig. 2 is the utility model pipeline interface arrangement schematic diagram；
Fig. 3 be the utility model pipeline in each parameter at x position schematic diagram.
Specific embodiment
In order to make the purpose of the utility model, technical solutions and advantages more clearly understood, below in conjunction with attached drawing and implementation
Example, the present invention is further described in detail.It should be appreciated that specific embodiment described herein is only used to explain
The utility model is not used to limit the utility model.In addition, institute in the various embodiments of the present invention described below
The technical characteristic being related to can be combined with each other as long as they do not conflict with each other.
Reference Fig. 1~Fig. 3, a kind of duct type active flow pulsation damping device for large reciprocating compressor, including
Surge tank pedestal 1, buffering tank 6, surge tank admission line 7, surge tank discharge duct 8 and pipeline group, wherein,
The buffering tank 6 is mounted on the surge tank pedestal 1；
The surge tank admission line 7 and surge tank discharge duct 8 are separately mounted on the buffering tank 6；
The pipeline group has more pipelines, they are respectively first branch pipeline 3, the second branch pipeline 2, first backflow
One end of 11 and second return tube 10 of pipeline, the first branch pipeline 3 and the second branch pipeline 2 passes through four-way connection A respectively
It is mounted on the surge tank admission line 7 with four-way connection B；
Described first one end for backflowing pipeline 11 is mounted on the surge tank admission line by described by four-way connection A
On 7 so that by first branch pipeline 3 and first backflow pipeline 11 flow after secondary gas flow and surge tank admission line 7 in
Primary air confluence when opposite in phase；
One end of second return tube 10 is mounted on the surge tank admission line 7 by described by four-way connection B
On, so that the secondary gas flow after the flowing of 2 and second return tube 10 of the second branch pipeline and the master in surge tank admission line 7
Opposite in phase when air-flow converges；
The first branch pipeline 3 and first pipeline 11 that backflows connect, to be inhibited from compressor out by pipe range
Air-flow odd multiple number of frequency pulsation；
2 and second return tube 10 of the second branch pipeline connects, to inhibit what is come out from compressor by pipe range
The pulsation of the even number overtones band of air-flow.
Further, pipe joint device is further included, the pipe joint device has among multiple pipe joints 9 and Duo Gen
Connecting tube, each pipe joint 9 are separately mounted on the buffering tank 6, and the every intermediate connection tube connects two institutes
State pipe joint 9, the first branch pipeline 3 is connected with first pipeline 11 that backflows by the pipe joint device, and described
Two tap lines 2 are connected with the second return tube 10 also by the pipe joint device.
Further, two are at least set to make up line and have what is made up line described in one in the buffering tank 6
Both ends are connected on a pipe joint 9, for connecting 3 and first return tube 11 of first branch pipeline, also
There are the both ends to make up line described in one to be connected on a pipe joint 9, for connecting the second branch pipe
2 and second return tube 10 of line, so as to inhibit the pulsation of the air-flow from compressor out by adjusting pipe range.It is shown in Fig. 1
Two make up line, and respectively first, which makes up line, 4 and second makes up line 5.
The present apparatus is using the pulsating nature of reciprocating compressor itself exhaust, and a branch and basis are connected in pipe-line system
It calculates and determines branch pipe range so that phase when converging after bypass flow with main road fluid of pulsating fluid is on the contrary, to reach
Active attenuation reciprocating compressor pipe-line system gas.
According under normal conditions, the pulsating quantity of stream pressure is the number of a very little relative to the average value of pressure in pipeline
Value, while the very little compared with pipe range of the pipe diameter in calculation for pipelines system of compressor, therefore can will be in reciprocating compressor pipeline
The flowing of fluid is reduced to one-dimensional steady flowing, thus we can obtain in cross-section pipe fluctuation pressure and fluid parameter with
And it is with the relationship of pipe range：
Wherein, x is the length of 0 position of distance, and 0 position refers to the position of four-way connection outflow end end,For pipe range x
Pressure fluctuation at position in pipeline, k=ω/a, ω are pulsation circular frequency, and a is the velocity of sound in pipeline, ρ0It is close for fluid at 0 position
Degree,For the velocity fluctuation in pipeline at 0 position, j is complex unit.
Ripple frequency is calculated according to the rotating speed of reciprocating compressor in actual device design：
Wherein, f is gas fundamental frequency, and n is reciprocating compressor rotating speed, and z is according to reciprocating compressor cylinder action side
Formula value, and single-acting formula value is 1, and double-acting type value is 2.
The gas frequency multiplication f of reciprocating compressormIt calculates：
Fm=m*f, m=1,2,3 ... (3)
Fundamental frequency pulsation, which inhibits required branch pipe range L to grow difference with main road pipe most short tube, to be calculated by formula (4)：
According to reciprocating compressor frequency multiplication calculating formula it is found that frequency multiplication inhibits required pipe range difference LmFor：
Work as LmDuring=L, m=1,2,3 ..., i.e. the pipe range difference of L can inhibit the pulsation of odd multiple number of frequency, similarly even-multiple
The pulsation of frequency can be usedL pipe ranges differences inhibits.
With the reciprocating compressor calculation specifications of certain operating mode, for example, certain double-acting type reciprocating compressor rotating speed 1200r/
Min, pressure at expulsion 20MPa, 127 DEG C of delivery temperature calculate gained
Since operation of reciprocating compressor frequency is relatively low, therefore gained L longer is calculated, because being arranged on the larger buffering in space
In tank, external pressure is surge tank internal pressure in tap line and each pipeline of the pipeline that backflows, therefore to bear pressure difference small for pipeline, can make
With the pipeline easy for installation such as high-pressure hose.Can corresponding pipe range be set according to the particular compressor speed of service in actual use,
With the pipe range to make up line, if compressor applying working condition can uniquely cancel the pipe joint 9 on surge tank tank body 6, by bypass duct
Line and the pipeline that backflows are set as a pipe, and directly required pipe range pipeline is connected on four-way interface.It, can when operating condition is not unique
Making up line for corresponding length is set in surge tank, and when in low frequency operating mode, the corresponding connector that makes up line of access increases institute
Need pipe range.
As it will be easily appreciated by one skilled in the art that the above is only the preferred embodiment of the utility model only, not
To limit the utility model, any modification made within the spirit and principles of the present invention, equivalent replacement and change
Into etc., it should be included within the scope of protection of this utility model.
Claims (3)
1. a kind of duct type active flow pulsation damping device for large reciprocating compressor, which is characterized in that including buffering
Tank bottom seat, buffering tank, surge tank admission line, surge tank discharge duct and pipeline group, wherein,
The buffering tank is mounted on the surge tank pedestal；
The surge tank admission line and surge tank discharge duct are separately mounted on the buffering tank；
The pipeline group has more pipelines, they are respectively first branch pipeline, the second branch pipeline, the first return tube and the
It is installed respectively by four-way connection A and four-way connection B one end of two return tubes, the first branch pipeline and the second branch pipeline
On the surge tank admission line；
One end of first return tube is mounted on by four-way connection A on the surge tank admission line by described；
One end of second return tube is mounted on by four-way connection B on the surge tank admission line by described；
The first branch pipeline and the connection of the first return tube, the second branch pipeline and the connection of the second return tube.
2. a kind of duct type active flow pulsation damping device for large reciprocating compressor according to claim 1,
It is characterized in that, further including pipe joint device, the pipe joint device has to be connected among multiple pipe joints and Duo Gen
Pipe, each pipe joint are separately mounted on the buffering tank, and the every intermediate connection tube connects two pipelines
Connector, the first branch pipeline and the first return tube are connected by the pipe joint device, the second branch pipeline and
Second return tube is connected also by the pipe joint device.
3. a kind of duct type active flow pulsation damping device for large reciprocating compressor according to claim 2,
It is characterized in that, two both ends point to make up line described in one that make up line and have at least are set in the buffering tank
It is not connected on a pipe joint, for connecting the first branch pipeline and the first return tube, also described in one
The both ends to make up line are connected on a pipe joint, are backflowed for connecting the second branch pipeline and second
Pipe.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN201721730718.1U CN207598456U (en) | 2017-12-13 | 2017-12-13 | A kind of duct type active flow pulsation damping device for large reciprocating compressor |
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| CN201721730718.1U CN207598456U (en) | 2017-12-13 | 2017-12-13 | A kind of duct type active flow pulsation damping device for large reciprocating compressor |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108087239A (en) * | 2017-12-13 | 2018-05-29 | 华中科技大学 | A kind of duct type active flow pulsation damping device for large reciprocating compressor |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108087239A (en) * | 2017-12-13 | 2018-05-29 | 华中科技大学 | A kind of duct type active flow pulsation damping device for large reciprocating compressor |
| CN108087239B (en) * | 2017-12-13 | 2024-04-05 | 华中科技大学 | Pipeline type active airflow pulsation attenuation device for large reciprocating compressor |
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