WO2019153871A1 - Pressure pulsation attenuating device, compressor and air conditioner - Google Patents

Pressure pulsation attenuating device, compressor and air conditioner Download PDF

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Publication number
WO2019153871A1
WO2019153871A1 PCT/CN2018/120369 CN2018120369W WO2019153871A1 WO 2019153871 A1 WO2019153871 A1 WO 2019153871A1 CN 2018120369 W CN2018120369 W CN 2018120369W WO 2019153871 A1 WO2019153871 A1 WO 2019153871A1
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WIPO (PCT)
Prior art keywords
pressure pulsation
compressor
main body
dampening device
pulsation dampening
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PCT/CN2018/120369
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French (fr)
Chinese (zh)
Inventor
刘华
张天翼
王磊
陈文卿
周明龙
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珠海格力电器股份有限公司
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Publication of WO2019153871A1 publication Critical patent/WO2019153871A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • F04C29/0035—Equalization of pressure pulses
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • F04C29/061—Silencers using overlapping frequencies, e.g. Helmholtz resonators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type

Definitions

  • the present invention relates to the field of air conditioning technology, and in particular to a pressure pulsation attenuating device, a compressor and an air conditioner.
  • the existing screw compressors have various uses, functions, forms and structures. The degree of vibration and noise and their propagation paths will be different. Specific analysis is required for specific structural forms, but the main sources of vibration and noise are still the same. of.
  • the noise of the screw compressor can be divided into mechanical noise and hydrodynamic noise according to the generation mechanism, and can be used as a sound source to induce periodic changes in the density of the surrounding air, thereby generating strong noise. At the same time, these two different kinds of noise will interact and superimpose. In addition to radiating noise directly to the outside, it will also stimulate the vibration of the compressor body and transmit it to the rest of the auxiliary equipment through the machine foot.
  • the mechanical noise of the screw compressor is effectively improved.
  • the working volume and the suction and exhaust chambers are periodically connected and disconnected to cause the working medium.
  • the strong airflow pulsation causes a drastic change (pressure pulsation) in the thermal characteristics of the working medium in the suction and exhaust chambers, and the induced hydrodynamic noise is the main source of the vibration noise of the screw compressor.
  • the pulsation of the airflow at the venting opening is more severe, so the vibration noise problem of the screw compressor can be effectively solved by reasonably controlling and improving the pressure pulsation amplitude of the gas medium in the exhaust chamber.
  • the induced mechanism of the pressure fluctuation of the screw compressor is: the pressure difference between the volume of the rotor cavity and the gas in the control volume of the exhaust chamber during the exhaust process and the periodic variation of the area of the exhaust orifice are the exhaust gas flow of the screw compressor.
  • the direct cause of the pulsation, and the periodic variation of the mass flow of the gas flowing into the exhaust chamber control volume through the exhaust orifice in the volume between the teeth of the rotor cavity causes a change in the gas thermal state parameter in the exhaust chamber, thereby causing the exhaust pressure pulsation.
  • Figure 1 shows the frequency domain value and time domain value of the compressor compressor discharge pressure pulsation under typical working conditions.
  • the fundamental frequency of the exhaust pressure pulsation is the meshing frequency of the yin and yang rotor, and the pressure pulsation amplitude at the rotor meshing frequency. It is much larger than the pressure pulsation amplitude at its integer multiple. Therefore, the vibration noise of the screw compressor can be reduced by reducing the pressure pulsation amplitude at the rotor meshing frequency in the exhaust chamber.
  • variable frequency screw compressor is directly driven by the variable frequency motor, and the capacity is adjusted by the change of the motor speed.
  • the variable speed screw compressor has a wide range of rotational speed during operation, and the rotor meshing frequency increases with the increase of the rotational speed, and the corresponding exhaust pressure pulsation frequency also changes continuously.
  • the traditional exhaust pressure pulsation dampening device can only achieve the attenuation of the pressure pulsation amplitude at a certain frequency. When the pressure pulsation frequency changes continuously, the attenuation effect is not obvious, and it can not meet the high temperature at different operating speeds. An urgent need for attenuation performance.
  • a primary object of the present invention is to provide a pressure pulsation dampening device, a compressor and an air conditioner to solve the problem of high vibration noise of the inverter screw in the prior art.
  • a pressure pulsation attenuating device includes: a main body having a fluid passage and a plurality of sets of through holes having different apertures and communicating with the fluid passage, and a plurality of through holes The groups are arranged in sequence along the length direction of the fluid passage; the outer casing is disposed on the outer circumference of the main body, the outer casing and the main body are surrounded to form a cavity, and the plurality of sets of through holes are in communication with the cavity.
  • the outer casing and the main body enclose a plurality of cavities connected in series, and the plurality of sets of through holes communicate with the plurality of cavities in a one-to-one correspondence to form a plurality of resonant cavities having different attenuation frequencies.
  • the outer casing and the main body enclose a plurality of mutually isolated cavities, and the plurality of sets of through holes communicate with the plurality of cavities in a one-to-one correspondence to form a plurality of resonant cavities having different attenuation frequencies.
  • each of the through hole groups includes a plurality of through holes, the plurality of through holes are arranged along a circumferential array of the main body, and the outer casing is an annular outer casing, and the annular outer casing is sleeved on the main body.
  • the natural frequency fr of the resonant cavity, the sound velocity C 0 of the fluid medium in the fluid passage, the wall thickness L of the main body, the radius a of each through hole of the through hole group, the length D of the main body, and the perforation rate P satisfy the following formula:
  • the perforation rate P of each group of through holes is different.
  • an oil drain structure is disposed on the outer casing.
  • oil drain structure is a drain hole.
  • the oil drain holes are one or two or more.
  • a compressor comprising a pressure pulsation dampening device, the pressure pulsation dampening device being the above-described pressure pulsation dampening device.
  • the compressor includes a main body and an exhaust chamber outlet disposed on the main body, and the pressure pulsation attenuating device is installed at the outlet of the exhaust chamber.
  • both ends of the attenuation device are provided with pressure detecting elements.
  • an air conditioner including a compressor which is the above-described compressor is provided.
  • the pressure pulsation dampening device of the present invention has a plurality of resonant cavities with different attenuation frequencies, which effectively broadens the resonance frequency band of the medium in the pressure pulsation dampening device, and uses the pressure pulsation dampening device of the present invention in the screw
  • the disturbance frequency can still be within the resonance frequency range of the medium in the pressure pulsation attenuating device, and the pressure pulsation amplitude is caused by the strong resonance of the medium in the pressure pulsation attenuating device.
  • the drastic reduction is caused, and the fluid dynamic noise induced thereby is remarkably reduced, thereby achieving the effect of reducing the vibration noise of the screw compressor.
  • the pressure pulsation attenuation device can reduce the amplitude of the gas pressure pulsation in the exhaust cavity of the screw compressor within a range of large speed variation, and effectively solve the vibration noise problem during the variable speed operation of the frequency conversion screw compressor.
  • Figure 1 is a schematic view showing the frequency domain value and the time domain value of the screw compressor discharge pressure pulsation under typical operating conditions
  • Figure 2 is a schematic cross-sectional view showing the pressure pulsation dampening device of the present invention
  • Figure 3 is a schematic front view showing the pressure pulsation dampening device of the present invention attached to a screw compressor;
  • Figure 4 is a schematic illustration of the pressure pulsation time domain values at the two pressure sensing elements of the compressor of the present invention.
  • spatially relative terms such as “above”, “above”, “on top”, “above”, etc., may be used herein to describe as in the drawings.
  • the exemplary term “above” can include both “over” and "under”.
  • the device can also be positioned in other different ways (rotated 90 degrees or at other orientations) and the corresponding description of the space used herein is interpreted accordingly.
  • a compressor is provided, and the compressor in this embodiment is preferably a variable frequency screw compressor.
  • the compressor in this embodiment includes a main body 40 and a pressure pulsation attenuating device provided on the main body 40, and the pressure pulsation attenuating device includes a main body 10 and a casing 20.
  • the main body 10 is provided with a fluid passage 11 and a plurality of sets of through holes 12 having different apertures and communicating with the fluid passage 11, and the plurality of sets of through holes 12 are sequentially arranged along the longitudinal direction of the fluid passage 11;
  • the outer casing 20 is disposed at the main body 10.
  • the outer casing 20 and the main body 10 enclose a cavity, and the plurality of sets of through holes 12 communicate with the cavity.
  • the pressure pulsation dampening device of the present invention has a plurality of resonant cavities 30 having different attenuation frequencies, which effectively broadens the resonance frequency band of the medium in the pressure pulsation dampening device.
  • the pressure pulsation dampening device in the embodiment is used in a screw compressor, the screw
  • the disturbance frequency can still be within the resonance frequency range of the medium in the pressure pulsation dampening device, and the pressure pulsation amplitude is greatly reduced by the strong resonance of the medium in the pressure pulsation dampening device.
  • the induced hydrodynamic noise is significantly reduced, thereby achieving the effect of reducing the vibration noise of the screw compressor.
  • the pressure pulsation attenuation device can reduce the amplitude of the gas pressure pulsation in the exhaust cavity of the screw compressor within a range of large speed variation, and effectively solve the vibration noise problem during the variable speed operation of the frequency conversion screw compressor.
  • the outer casing 20 is formed on the outer periphery of the main body 10 to form a plurality of cavities connected in series, and the plurality of sets of through holes 12 correspond to the plurality of cavities.
  • the grounds are connected to form a plurality of resonant cavities 30 having different attenuation frequencies.
  • the plurality of series-connected cavities in the present invention can be obtained by directly enclosing the outer casing 20 in a cavity formed by the outer periphery of the main body 10 provided with the plurality of through-hole groups 12, and the structure is simple and convenient to implement, as shown in the figure. 1 is shown.
  • the outer casing 20 may be formed on the outer periphery of the main body 10 to form a plurality of mutually isolated cavities, and the plurality of sets of through-hole groups 12 are connected in one-to-one correspondence with the plurality of cavities. It is within the scope of the present invention to form a plurality of resonant cavities 30 having different attenuation frequencies as long as they are other modifications under the concept of the present invention.
  • the resonant cavity 30 is set to three.
  • the resonant cavity 30 may be set to two or more, specifically according to The demand for screw compressors is set.
  • the main body 10 in this embodiment is a centrally-opened pipe.
  • the central opening of the pipe forms the fluid passage 11 described above, and the through-hole group 12 having different apertures is formed on the pipe wall of the centrally-opened pipe. Simple and easy to implement.
  • each of the through hole groups 12 in this embodiment includes a plurality of through holes, and the plurality of through holes are arranged along a circumferential array of the main body 10.
  • the outer casing 20 is an annular outer casing, and the annular outer casing is sleeved on The main body 10 is provided with a resonant cavity 30 formed on the outer periphery of the main body 10. The structure is simple and convenient to implement.
  • the outer casing 20 of the embodiment is provided with an oil draining structure 21, and the lubricating oil in the resonant cavity 30 is conveniently discharged by the action of the oil draining structure 21, so that the lubricating oil in the resonant cavity 30 can be freely circulated and resonated.
  • the lubricating oil in the chamber 30 is discharged from the drain structure 21 of the airflow pulsation attenuator in time.
  • the oil leakage structure 21 in the embodiment is a drain hole, and in actual design, the oil drain hole is one or two or more.
  • the pressure pulsation attenuating device is installed at the outlet end 41 of the screw compressor exhaust chamber, and pressure detection is applied at both ends of the pressure pulsation attenuating device.
  • the component 50 is preferably a high frequency pressure sensor, wherein the right side in FIG. 3 is a high frequency pressure sensor P1 and the left side is a high frequency pressure sensor P2.
  • the phase difference of the pressure signal measured by the two pressure sensors P1 and P2 is combined with the installation distance of the pressure sensor to obtain the actual sound velocity of the working medium in the fluid channel 11, and the structural parameters are calculated according to the calculation method of the natural frequency of the single resonant cavity 30. design.
  • the natural frequency fr of the resonant cavity 30, the sound velocity C 0 of the fluid medium in the fluid passage 11, the wall thickness L of the main body 10, the radius a of each through hole of the through hole group 12, the length D of the main body 10, and the perforation rate P satisfy.
  • the perforation rate P is a value obtained by dividing the sum of the areas of the respective through holes on each group of the through holes 12 by the total area of the corresponding opening portion.
  • the perforation rate P of each group of through-hole groups 12 is different, and it is convenient to form the resonant cavity 30 having different attenuation frequencies.
  • the performance of the designed broadband pressure pulsation attenuation device can be analyzed and calculated by the pressure signals measured by the two pressure sensors P1 and P2. It can be seen from Fig. 4 that after the pressure pulsation dampening device is installed, the pressure pulsation amplitude in the exhaust cavity of the screw compressor can be effectively reduced, which satisfies the noise reduction requirement of the inverter screw compressor.
  • an air conditioner is provided, and the air conditioner in this embodiment includes a compressor, and the compressor is the above-described compressor.
  • the main body of the pressure pulsation attenuating device of the present invention has a through hole, and a through hole group is formed on the wall of the main body to communicate with a cavity on the outer casing to form a pressure pulsation resonance cavity, and the pressure pulsation amplitude is attenuated, thereby effectively reducing hydrodynamic noise.
  • the device In the frequency range, the exhaust pressure pulsation amplitude during the variable speed operation can be effectively reduced, and the induced hydrodynamic noise is significantly reduced.
  • the device has a simple structure and low cost, and does not require major changes to the compressor structure and can be installed and used.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

A pressure pulsation attenuating device, a compressor comprising the pressure pulsation attenuating device and an air conditioner. The pressure pulsation attenuating device comprises: a main body (10), the main body (10) being provided thereon with a fluid passage (11) and a plurality of through hole sets (12) that have different apertures and that communicate with the fluid passage (11), the plurality of through hole sets (12) being arranged in sequence along the length direction of the fluid passage (11); an outer housing (20), the outer housing (20) being disposed at the outer circumference of the main body (10), and the outer housing (20) and the main body (10) enclosing to form a cavity, while the plurality of through hole sets (12) communicate with the cavity.

Description

压力脉动衰减装置、压缩机及空调器Pressure pulsation attenuating device, compressor and air conditioner 技术领域Technical field
本发明涉及空调技术领域，具体而言，涉及一种压力脉动衰减装置、压缩机及空调器。The present invention relates to the field of air conditioning technology, and in particular to a pressure pulsation attenuating device, a compressor and an air conditioner.
背景技术Background technique
现有的螺杆压缩机的用途、功能、形式及结构多种多样，振动噪声程度及其传播路径会有所不同，需针对具体的结构形式进行具体分析，但其主要的振动噪声源仍是相同的。螺杆压缩机的噪声按产生机理可以分为机械性噪声和流体动力性噪声，均可作为声源激励，引起周围空气密度的周期性变化，从而产生强烈的噪音。同时，这两种不同性质的噪声还会相互作用、叠加，除了直接向外界辐射噪声外，还会激励压缩机的机体振动，并通过机脚向其余附属设备传递。The existing screw compressors have various uses, functions, forms and structures. The degree of vibration and noise and their propagation paths will be different. Specific analysis is required for specific structural forms, but the main sources of vibration and noise are still the same. of. The noise of the screw compressor can be divided into mechanical noise and hydrodynamic noise according to the generation mechanism, and can be used as a sound source to induce periodic changes in the density of the surrounding air, thereby generating strong noise. At the same time, these two different kinds of noise will interact and superimpose. In addition to radiating noise directly to the outside, it will also stimulate the vibration of the compressor body and transmit it to the rest of the auxiliary equipment through the machine foot.
随着机械加工精度的提高和装配工艺的改善，螺杆压缩机的机械性噪音得到有效改善，但是在螺杆压缩机运行过程中工作容积与吸、排气腔周期性的连通、脱离会引起工作介质强烈的气流脉动，使得吸、排气腔内工作介质的热力特性产生剧烈的变化(压力脉动)，由此诱发的流体动力性噪音是螺杆压缩机振动噪音的主要源头。其中排气孔口处的气流脉动程度更为剧烈，因此可通过合理控制和改善排气腔内气体介质的压力脉动幅值来效解决螺杆压缩机的振动噪音问题。With the improvement of machining precision and the improvement of assembly process, the mechanical noise of the screw compressor is effectively improved. However, during the operation of the screw compressor, the working volume and the suction and exhaust chambers are periodically connected and disconnected to cause the working medium. The strong airflow pulsation causes a drastic change (pressure pulsation) in the thermal characteristics of the working medium in the suction and exhaust chambers, and the induced hydrodynamic noise is the main source of the vibration noise of the screw compressor. The pulsation of the airflow at the venting opening is more severe, so the vibration noise problem of the screw compressor can be effectively solved by reasonably controlling and improving the pressure pulsation amplitude of the gas medium in the exhaust chamber.
螺杆压缩机排气压力脉动的诱发机理为：排气过程中转子腔齿间容积与排气腔控制容积内气体的压力差和排气孔口面积的周期性变化是导致螺杆压缩机排气气流脉动的直接诱因，而转子腔齿间容积内经由排气孔口流入排气腔控制容积内的气体质量流量的周期性变化导致了排气腔内气体热力状态参数的变化，进而引起排气压力脉动。图1给出了典型工况下螺杆压缩机排气压力脉动的频域值和时域值，排气压力脉动的基频为阴阳转子的啮合频率，且处于转子啮合频率下的压力脉动幅值远远大于处于其整数倍频率下的压力脉动幅值。因此可通过降低排气腔内处于转子啮合频率下的压力脉动幅来降低螺杆压缩机的振动噪音。The induced mechanism of the pressure fluctuation of the screw compressor is: the pressure difference between the volume of the rotor cavity and the gas in the control volume of the exhaust chamber during the exhaust process and the periodic variation of the area of the exhaust orifice are the exhaust gas flow of the screw compressor. The direct cause of the pulsation, and the periodic variation of the mass flow of the gas flowing into the exhaust chamber control volume through the exhaust orifice in the volume between the teeth of the rotor cavity causes a change in the gas thermal state parameter in the exhaust chamber, thereby causing the exhaust pressure pulsation. Figure 1 shows the frequency domain value and time domain value of the compressor compressor discharge pressure pulsation under typical working conditions. The fundamental frequency of the exhaust pressure pulsation is the meshing frequency of the yin and yang rotor, and the pressure pulsation amplitude at the rotor meshing frequency. It is much larger than the pressure pulsation amplitude at its integer multiple. Therefore, the vibration noise of the screw compressor can be reduced by reducing the pressure pulsation amplitude at the rotor meshing frequency in the exhaust chamber.
变频螺杆压缩机由变频电机直接驱动，通过电动机转速的变化实现容量调节。较定频螺杆压缩机而言，变频螺杆压缩机在运行过程中转速变化范围宽，转子啮合频率会随转速的增加而增加，相应的排气压力脉动频率也会不断变化。而传统的排气压力脉动衰减装置只能在某一特定频率下实现压力脉动幅值的衰减，当压力脉动频率不断变化时其衰减效果并不明显，无法满足在不同运行转速下均保持较高衰减性能的迫切需求。The variable frequency screw compressor is directly driven by the variable frequency motor, and the capacity is adjusted by the change of the motor speed. Compared with the fixed-frequency screw compressor, the variable speed screw compressor has a wide range of rotational speed during operation, and the rotor meshing frequency increases with the increase of the rotational speed, and the corresponding exhaust pressure pulsation frequency also changes continuously. The traditional exhaust pressure pulsation dampening device can only achieve the attenuation of the pressure pulsation amplitude at a certain frequency. When the pressure pulsation frequency changes continuously, the attenuation effect is not obvious, and it can not meet the high temperature at different operating speeds. An urgent need for attenuation performance.
发明内容Summary of the invention
本发明的主要目的在于提供一种压力脉动衰减装置、压缩机及空调器，以解决现有技术中的变频螺杆的振动噪音高的问题。SUMMARY OF THE INVENTION A primary object of the present invention is to provide a pressure pulsation dampening device, a compressor and an air conditioner to solve the problem of high vibration noise of the inverter screw in the prior art.
为了实现上述目的，根据本发明的一个方面，提供了一种压力脉动衰减装置，包括：主体，主体上设置有流体通道和多组孔径不同且与流体通道连通的通孔组，多组通孔组沿流体通道的长度方向依次布置；外壳，外壳设置在主体的外周，外壳与主体围设形成空腔，多组通孔组与空腔连通。In order to achieve the above object, according to an aspect of the present invention, a pressure pulsation attenuating device includes: a main body having a fluid passage and a plurality of sets of through holes having different apertures and communicating with the fluid passage, and a plurality of through holes The groups are arranged in sequence along the length direction of the fluid passage; the outer casing is disposed on the outer circumference of the main body, the outer casing and the main body are surrounded to form a cavity, and the plurality of sets of through holes are in communication with the cavity.
进一步地，外壳与主体围设形成多个串联连通的空腔，多组通孔组与多个空腔一一对应地连通以形成多种衰减频率不同的共振腔。Further, the outer casing and the main body enclose a plurality of cavities connected in series, and the plurality of sets of through holes communicate with the plurality of cavities in a one-to-one correspondence to form a plurality of resonant cavities having different attenuation frequencies.
进一步地，外壳与主体围设形成多个相互隔离的空腔，多组通孔组与多个空腔一一对应地连通以形成多种衰减频率不同的共振腔。Further, the outer casing and the main body enclose a plurality of mutually isolated cavities, and the plurality of sets of through holes communicate with the plurality of cavities in a one-to-one correspondence to form a plurality of resonant cavities having different attenuation frequencies.
进一步地，各通孔组均包括多个通孔，多个通孔沿主体的周向阵列布置，外壳为环形外壳，环形外壳套设在主体上。Further, each of the through hole groups includes a plurality of through holes, the plurality of through holes are arranged along a circumferential array of the main body, and the outer casing is an annular outer casing, and the annular outer casing is sleeved on the main body.
进一步地，共振腔的固有频率fr、流体通道内的流体介质声速C 0、主体的壁厚L、通孔组的各个通孔的半径a、主体的长度D、穿孔率P满足如下公式：
Figure PCTCN2018120369-appb-000001
Further, the natural frequency fr of the resonant cavity, the sound velocity C 0 of the fluid medium in the fluid passage, the wall thickness L of the main body, the radius a of each through hole of the through hole group, the length D of the main body, and the perforation rate P satisfy the following formula:
Figure PCTCN2018120369-appb-000001
进一步地，各组通孔组的穿孔率P不同。Further, the perforation rate P of each group of through holes is different.
进一步地，外壳上设置有泄油结构。Further, an oil drain structure is disposed on the outer casing.
进一步地，泄油结构为泄油孔。Further, the oil drain structure is a drain hole.
进一步地，泄油孔为一个或两个或两个以上。根据本发明的另一方面，提供了一种压缩机，包括压力脉动衰减装置，压力脉动衰减装置为上述的压力脉动衰减装置。Further, the oil drain holes are one or two or more. According to another aspect of the present invention, there is provided a compressor comprising a pressure pulsation dampening device, the pressure pulsation dampening device being the above-described pressure pulsation dampening device.
进一步地，压缩机包括主机和设置在主机上的排气腔出口，压力脉动衰减装置安装在排气腔出口处。Further, the compressor includes a main body and an exhaust chamber outlet disposed on the main body, and the pressure pulsation attenuating device is installed at the outlet of the exhaust chamber.
进一步地，衰减装置的两端均设置有压力检测元件。Further, both ends of the attenuation device are provided with pressure detecting elements.
根据本发明的再一方面，提供了一种空调器，包括压缩机，压缩机为上述的压缩机。According to still another aspect of the present invention, an air conditioner including a compressor which is the above-described compressor is provided.
应用本发明的技术方案，本发明的压力脉动衰减装置具有多种衰减频率不同的共振腔，有效拓宽了压力脉动衰减装置内介质的共振频带，当将本发明中的压力脉动衰减装置使用在螺杆压缩机中，螺杆压缩机的转子啮合率随转速发生变化时，扰动频率仍可处于压力脉动衰减装置内介质的共振频率范围内时，通过压力脉动衰减装置内介质的强烈共振使得压力脉动幅值大幅降低，由此诱发的流体动力性噪音显著减小，进而达到降低螺杆压缩机的振动噪音的效果。According to the technical solution of the present invention, the pressure pulsation dampening device of the present invention has a plurality of resonant cavities with different attenuation frequencies, which effectively broadens the resonance frequency band of the medium in the pressure pulsation dampening device, and uses the pressure pulsation dampening device of the present invention in the screw In the compressor, when the rotor meshing rate of the screw compressor changes with the rotational speed, the disturbance frequency can still be within the resonance frequency range of the medium in the pressure pulsation attenuating device, and the pressure pulsation amplitude is caused by the strong resonance of the medium in the pressure pulsation attenuating device. The drastic reduction is caused, and the fluid dynamic noise induced thereby is remarkably reduced, thereby achieving the effect of reducing the vibration noise of the screw compressor.
可见，通过压力脉动衰减装置的作用，可在较大转速变化范围内实现螺杆压缩机排气腔内气体压力脉动幅值的降低，有效解决了变频螺杆压缩机变转速运行过程中的振动噪音问题。It can be seen that the pressure pulsation attenuation device can reduce the amplitude of the gas pressure pulsation in the exhaust cavity of the screw compressor within a range of large speed variation, and effectively solve the vibration noise problem during the variable speed operation of the frequency conversion screw compressor.
附图说明DRAWINGS
构成本申请的一部分的说明书附图用来提供对本发明的进一步理解，本发明的示意性实施例及其说明用于解释本发明，并不构成对本发明的不当限定。在附图中：The accompanying drawings, which are incorporated in the claims of the claims In the drawing:
图1示意性示出了典型工况下螺杆压缩机排气压力脉动的频域值和时域值；Figure 1 is a schematic view showing the frequency domain value and the time domain value of the screw compressor discharge pressure pulsation under typical operating conditions;
图2示意性示出了本发明的压力脉动衰减装置的剖视图；Figure 2 is a schematic cross-sectional view showing the pressure pulsation dampening device of the present invention;
图3示意性示出了本发明的压力脉动衰减装置连接在螺杆压缩机上时的主视图；以及Figure 3 is a schematic front view showing the pressure pulsation dampening device of the present invention attached to a screw compressor;
图4示意性示出了本发明的压缩机的两个压力检测元件处的压力脉动时域值。Figure 4 is a schematic illustration of the pressure pulsation time domain values at the two pressure sensing elements of the compressor of the present invention.
其中，上述附图包括以下附图标记：Wherein, the above figures include the following reference numerals:
10、主体；11、流体通道；12、通孔组；20、外壳；21、泄油结构；30、共振腔；40、主机；41、排气腔出口；50、压力检测元件。10, the main body; 11, the fluid channel; 12, the through hole group; 20, the outer casing; 21, the oil drain structure; 30, the resonant cavity; 40, the host; 41, the exhaust chamber outlet; 50, the pressure detecting element.
具体实施方式Detailed ways
需要说明的是，在不冲突的情况下，本申请中的实施例及实施例中的特征可以相互组合。下面将参考附图并结合实施例来详细说明本发明。It should be noted that the embodiments in the present application and the features in the embodiments may be combined with each other without conflict. The invention will be described in detail below with reference to the drawings in conjunction with the embodiments.
需要注意的是，这里所使用的术语仅是为了描述具体实施方式，而非意图限制根据本申请的示例性实施方式。如在这里所使用的，除非上下文另外明确指出，否则单数形式也意图包括复数形式，此外，还应当理解的是，当在本说明书中使用术语“包含”和/或“包括”时，其指明存在特征、步骤、操作、器件、组件和/或它们的组合。It is to be noted that the terminology used herein is for the purpose of describing particular embodiments, and is not intended to limit the exemplary embodiments. As used herein, the singular " " " " " " There are features, steps, operations, devices, components, and/or combinations thereof.
需要说明的是，本申请的说明书和权利要求书及上述附图中的术语“第一”、“第二”等是用于区别类似的对象，而不必用于描述特定的顺序或先后次序。应该理解这样使用的数据在适当情况下可以互换，以便这里描述的本申请的实施方式例如能够以除了在这里图示或描述的那些以外的顺序实施。此外，术语“包括”和“具有”以及他们的任何变形，意图在于覆盖不排他的包含，例如，包含了一系列步骤或单元的过程、方法、***、产品或设备不必限于清楚地列出的那些步骤或单元，而是可包括没有清楚地列出的或对于这些过程、方法、产品或设备固有的其它步骤或单元。It should be noted that the terms "first", "second" and the like in the specification and claims of the present application and the above-mentioned drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or order. It is to be understood that the data so used may be interchanged as appropriate, such that the embodiments of the present application described herein can be implemented, for example, in a sequence other than those illustrated or described herein. In addition, the terms "comprises" and "comprises" and "the" and "the" are intended to cover a non-exclusive inclusion, for example, a process, method, system, product, or device that comprises a series of steps or units is not necessarily limited to Those steps or units may include other steps or units not explicitly listed or inherent to such processes, methods, products or devices.
为了便于描述，在这里可以使用空间相对术语，如“在……之上”、“在……上方”、“在……上表面”、“上面的”等，用来描述如在图中所示的一个器件或特征与其他器件或特征的空间位置关系。应当理解的是，空间相对术语旨在包含除了器件在图中所描述的方位之外的在使用或操作中的不同方位。例如，如果附图中的器件被倒置，则描述为“在其他器件或构造上方”或“在其他器件或构造之上”的器件之后将被定位为“在其他器件或构造下方”或“在其他器件或构造之下”。因而，示例性术语“在……上方”可以包括“在……上方”和“在……下方”两种方位。该器件也可以其他不同方式定位(旋转90度或处于其他方位)，并且对这里所使用的空间相对描述作出相应解释。For convenience of description, spatially relative terms such as "above", "above", "on top", "above", etc., may be used herein to describe as in the drawings. The spatial positional relationship of one device or feature to other devices or features. It will be understood that the spatially relative terms are intended to encompass different orientations in use or operation in addition to the orientation of the device described. For example, if the device in the figures is inverted, the device described as "above other devices or configurations" or "above other devices or configurations" will be positioned "below other devices or configurations" or "at Under other devices or configurations." Thus, the exemplary term "above" can include both "over" and "under". The device can also be positioned in other different ways (rotated 90 degrees or at other orientations) and the corresponding description of the space used herein is interpreted accordingly.
参见图2至图4所示，根据本发明的实施例，提供了一种压缩机，本实施例中的压缩机优选为变频螺杆压缩机。Referring to Figures 2 to 4, in accordance with an embodiment of the present invention, a compressor is provided, and the compressor in this embodiment is preferably a variable frequency screw compressor.
本实施例中的压缩机包括主机40和设置在主机40上的压力脉动衰减装置，该压力脉动衰减装置包括主体10和外壳20。其中，主体10上设置有流体通道11和多组孔径不同且与流体通道11连通的通孔组12，多组通孔组12沿流体通道11的长度方向依次布置；外壳20设置在主体10的外周，外壳20与主体10围设形成空腔，多组通孔组12与空腔连通，压缩机工作时，噪音通过压力脉动衰减装置，可以形成多种衰减频率不同的共振腔30。The compressor in this embodiment includes a main body 40 and a pressure pulsation attenuating device provided on the main body 40, and the pressure pulsation attenuating device includes a main body 10 and a casing 20. The main body 10 is provided with a fluid passage 11 and a plurality of sets of through holes 12 having different apertures and communicating with the fluid passage 11, and the plurality of sets of through holes 12 are sequentially arranged along the longitudinal direction of the fluid passage 11; the outer casing 20 is disposed at the main body 10. In the outer periphery, the outer casing 20 and the main body 10 enclose a cavity, and the plurality of sets of through holes 12 communicate with the cavity. When the compressor is in operation, the noise passes through the pressure pulsation attenuating device, and a plurality of resonant cavities 30 having different attenuation frequencies can be formed.
本发明的压力脉动衰减装置具有多种衰减频率不同的共振腔30，有效拓宽了压力脉动衰减装置内介质的共振频带，当将本实施例中的压力脉动衰减装置使用在螺杆压缩机中，螺杆压缩机的转子啮合率随转速发生变化时，扰动频率仍可处于压力脉动衰减装置内介质的共振频率范围内时，通过压力脉动衰减装置内介质的强烈共振使得压力脉动幅值大幅降低，由此诱发的流体动力性噪音显著减小，进而达到降低螺杆压缩机的振动噪音的效果。The pressure pulsation dampening device of the present invention has a plurality of resonant cavities 30 having different attenuation frequencies, which effectively broadens the resonance frequency band of the medium in the pressure pulsation dampening device. When the pressure pulsation dampening device in the embodiment is used in a screw compressor, the screw When the rotor meshing rate of the compressor changes with the rotational speed, the disturbance frequency can still be within the resonance frequency range of the medium in the pressure pulsation dampening device, and the pressure pulsation amplitude is greatly reduced by the strong resonance of the medium in the pressure pulsation dampening device. The induced hydrodynamic noise is significantly reduced, thereby achieving the effect of reducing the vibration noise of the screw compressor.
可见，通过压力脉动衰减装置的作用，可在较大转速变化范围内实现螺杆压缩机排气腔内气体压力脉动幅值的降低，有效解决了变频螺杆压缩机变转速运行过程中的振动噪音问题。It can be seen that the pressure pulsation attenuation device can reduce the amplitude of the gas pressure pulsation in the exhaust cavity of the screw compressor within a range of large speed variation, and effectively solve the vibration noise problem during the variable speed operation of the frequency conversion screw compressor.
实际设计时，在本发明的一种优选的实施例中，可是使得外壳20在主体10的外周围设形成多个串联连通的空腔，多组通孔组12与多个空腔一一对应地连通以形成多种衰减频率不同的共振腔30。本发明中的多个串联连通的空腔可以通过外壳20直接扣盖在主体10的设置有上述的多个通孔组12的外周围设形成的空腔得到，结构简单，便于实现，如图1所示。In a preferred embodiment of the present invention, in a preferred embodiment of the present invention, the outer casing 20 is formed on the outer periphery of the main body 10 to form a plurality of cavities connected in series, and the plurality of sets of through holes 12 correspond to the plurality of cavities. The grounds are connected to form a plurality of resonant cavities 30 having different attenuation frequencies. The plurality of series-connected cavities in the present invention can be obtained by directly enclosing the outer casing 20 in a cavity formed by the outer periphery of the main body 10 provided with the plurality of through-hole groups 12, and the structure is simple and convenient to implement, as shown in the figure. 1 is shown.
在本发明的另一种优选的实施例中，还可以使得外壳20在主体10的外周围设形成多个相互隔离的空腔，多组通孔组12与多个空腔一一对应地连通以形成多种衰减频率不同的共振腔30，只要是在本发明的构思下的其他变形方式，均在本发明的保护范围之内。In another preferred embodiment of the present invention, the outer casing 20 may be formed on the outer periphery of the main body 10 to form a plurality of mutually isolated cavities, and the plurality of sets of through-hole groups 12 are connected in one-to-one correspondence with the plurality of cavities. It is within the scope of the present invention to form a plurality of resonant cavities 30 having different attenuation frequencies as long as they are other modifications under the concept of the present invention.
如图1所示，在本实施例中，将共振腔30设置为3个，当然，在本发明的其他实施例中，还可以将共振腔30设置为两个或者三个以上，具体可以根据螺杆压缩机的使用需求设定。As shown in FIG. 1 , in the embodiment, the resonant cavity 30 is set to three. Of course, in other embodiments of the present invention, the resonant cavity 30 may be set to two or more, specifically according to The demand for screw compressors is set.
本实施例中的主体10为一个中心开孔的管道，该管道的中心开孔形成上述的流体通道11，在中心开孔的管道的管壁上开设上述的孔径不同的通孔组12，结构简单，便于实现。The main body 10 in this embodiment is a centrally-opened pipe. The central opening of the pipe forms the fluid passage 11 described above, and the through-hole group 12 having different apertures is formed on the pipe wall of the centrally-opened pipe. Simple and easy to implement.
参见图2所示，本实施例中的各通孔组12均包括多个通孔，多个通孔沿主体10的周向阵列布置，对应地，外壳20为环形外壳，环形外壳套设在主体10上，便于在主体10的外周围设形成共振腔30，结构简单，便于实现。Referring to FIG. 2, each of the through hole groups 12 in this embodiment includes a plurality of through holes, and the plurality of through holes are arranged along a circumferential array of the main body 10. Correspondingly, the outer casing 20 is an annular outer casing, and the annular outer casing is sleeved on The main body 10 is provided with a resonant cavity 30 formed on the outer periphery of the main body 10. The structure is simple and convenient to implement.
考虑到螺杆压缩机在工作过程中含有微量润滑，会影响共振腔30的体积，使得共振腔30内介质的共振频率偏离设计值，从而影响到压力脉动的衰减效果。因而本实施例中的外壳20上设置有泄油结构21，通过该泄油结构21的作用，便于将共振腔30内的润滑油排出，保证共振腔30内的润滑油能自由流通，使共振腔30内的润滑油及时从气流脉动衰减器的泄油结构21排出。Considering that the screw compressor contains a small amount of lubrication during the working process, the volume of the resonant cavity 30 is affected, so that the resonance frequency of the medium in the resonant cavity 30 deviates from the design value, thereby affecting the attenuation effect of the pressure pulsation. Therefore, the outer casing 20 of the embodiment is provided with an oil draining structure 21, and the lubricating oil in the resonant cavity 30 is conveniently discharged by the action of the oil draining structure 21, so that the lubricating oil in the resonant cavity 30 can be freely circulated and resonated. The lubricating oil in the chamber 30 is discharged from the drain structure 21 of the airflow pulsation attenuator in time.
优选地，本实施例中的泄油结构21为泄油孔，实际设计时，泄油孔为一个或两个或两个以上。Preferably, the oil leakage structure 21 in the embodiment is a drain hole, and in actual design, the oil drain hole is one or two or more.
为尽可能的靠近螺杆压缩机的压力脉动的产生源头，本实施例中将压力脉动衰减装置安装在螺杆压缩机排气腔出口41处，并在压力脉动衰减装置的两端加设了压力检测元件50，该压力检测元件优选为高频压力传感器，其中位于图3中的右侧为高频压力传感器P1，左侧为高频压力传感器P2。通过P1和P2两个压力传感器测得的压力信号的相位差结合压力传感器的安装距离可得到流体通道11内工作介质的实际声速，根据单个共振腔30的固有频率的计算方法对其结构参数进行设计。In order to be as close as possible to the source of the pressure pulsation of the screw compressor, in this embodiment, the pressure pulsation attenuating device is installed at the outlet end 41 of the screw compressor exhaust chamber, and pressure detection is applied at both ends of the pressure pulsation attenuating device. The component 50 is preferably a high frequency pressure sensor, wherein the right side in FIG. 3 is a high frequency pressure sensor P1 and the left side is a high frequency pressure sensor P2. The phase difference of the pressure signal measured by the two pressure sensors P1 and P2 is combined with the installation distance of the pressure sensor to obtain the actual sound velocity of the working medium in the fluid channel 11, and the structural parameters are calculated according to the calculation method of the natural frequency of the single resonant cavity 30. design.
其中，共振腔30的固有频率fr、流体通道11内的流体介质声速C 0、主体10的壁厚L、通孔组12的各个通孔的半径a、主体10的长度D、穿孔率P满足公式
Figure PCTCN2018120369-appb-000002
其中，穿孔率P是指各组通孔组12上的各个通孔的面积之和除以对应的开孔部位的全面积得到的值。且各组通孔组12的穿孔率P不同，便于形成衰减频率不同的共振腔30。 The natural frequency fr of the resonant cavity 30, the sound velocity C 0 of the fluid medium in the fluid passage 11, the wall thickness L of the main body 10, the radius a of each through hole of the through hole group 12, the length D of the main body 10, and the perforation rate P satisfy. formula
Figure PCTCN2018120369-appb-000002
The perforation rate P is a value obtained by dividing the sum of the areas of the respective through holes on each group of the through holes 12 by the total area of the corresponding opening portion. Moreover, the perforation rate P of each group of through-hole groups 12 is different, and it is convenient to form the resonant cavity 30 having different attenuation frequencies.
此外，还可通过P1和P2两个压力传感器测得的压力信号对设计所得的宽频压力脉动衰减装置的性能进行分析计算。从图4可以看出，安装压力脉动衰减装置后，可使螺杆压缩机的排气腔内的压力脉动幅值得到有效降低，满足了变频螺杆压缩机的降噪需求。In addition, the performance of the designed broadband pressure pulsation attenuation device can be analyzed and calculated by the pressure signals measured by the two pressure sensors P1 and P2. It can be seen from Fig. 4 that after the pressure pulsation dampening device is installed, the pressure pulsation amplitude in the exhaust cavity of the screw compressor can be effectively reduced, which satisfies the noise reduction requirement of the inverter screw compressor.
根据本发明的另一方面，提供了一种空调器，本实施例中的空调器包括压缩机，压缩机为上述的压缩机。According to another aspect of the present invention, an air conditioner is provided, and the air conditioner in this embodiment includes a compressor, and the compressor is the above-described compressor.
从以上的描述中，可以看出，本发明上述的实施例实现了如下技术效果：From the above description, it can be seen that the above-described embodiments of the present invention achieve the following technical effects:
本发明的压力脉动衰减装置的主体的中心穿孔，主体的壁上开设有通孔组与外壳上的空腔连通，形成压力脉动共振腔，衰减压力脉动幅值，可有效降低流体动力性噪音。通过发明一种宽频带排气压力脉动衰减装置，由于该压力脉动衰减装置具有较宽的共振频率范围，当螺杆压缩机运行变速变化时，转子啮合频率仍可处于压力脉动衰减装置内介质的共振频率范围内，使得变转速运行过程中的排气压力脉动幅值均可得到有效的降低，由此诱发的流体动力性噪音显著减小。同时该装置结构简单，成本低，不需要对压缩机结构进行较大的变更及可安装使用。The main body of the pressure pulsation attenuating device of the present invention has a through hole, and a through hole group is formed on the wall of the main body to communicate with a cavity on the outer casing to form a pressure pulsation resonance cavity, and the pressure pulsation amplitude is attenuated, thereby effectively reducing hydrodynamic noise. By inventing a wide-band exhaust pressure pulsation dampening device, since the pressure pulsation dampening device has a wide resonant frequency range, when the screw compressor operates at a shifting change, the rotor meshing frequency can still be in the resonance of the medium in the pressure pulsation dampening device. In the frequency range, the exhaust pressure pulsation amplitude during the variable speed operation can be effectively reduced, and the induced hydrodynamic noise is significantly reduced. At the same time, the device has a simple structure and low cost, and does not require major changes to the compressor structure and can be installed and used.
以上所述仅为本发明的优选实施例而已，并不用于限制本发明，对于本领域的技术人员来说，本发明可以有各种更改和变化。凡在本发明的精神和原则之内，所作的任何修改、等同替换、改进等，均应包含在本发明的保护范围之内。The above description is only the preferred embodiment of the present invention, and is not intended to limit the present invention, and various modifications and changes can be made to the present invention. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and scope of the present invention are intended to be included within the scope of the present invention.

Claims (13)

  1. 一种压力脉动衰减装置，其特征在于，包括：A pressure pulsation attenuating device, comprising:
    主体(10)，所述主体(10)上设置有流体通道(11)和多组孔径不同且与所述流体通道(11)连通的通孔组(12)，多组所述通孔组(12)沿所述流体通道(11)的长度方向依次布置；a body (10), wherein the body (10) is provided with a fluid passage (11) and a plurality of sets of through holes (12) having different apertures and communicating with the fluid passage (11), and the plurality of sets of the through holes ( 12) sequentially arranged along the length direction of the fluid passage (11);
    外壳(20)，所述外壳(20)设置在所述主体(10)的外周，所述外壳(20)与所述主体(10)围设形成空腔，多组所述通孔组(12)与所述空腔连通。a casing (20) disposed on an outer circumference of the body (10), the casing (20) and the body (10) enclosing a cavity, and a plurality of sets of the through hole groups (12) ) in communication with the cavity.
  2. 根据权利要求1所述的压力脉动衰减装置，其特征在于，所述外壳(20)与所述主体(10)围设形成多个串联连通的空腔，多组所述通孔组(12)与多个所述空腔一一对应地连通以形成多种衰减频率不同的共振腔(30)。The pressure pulsation dampening device according to claim 1, wherein the outer casing (20) and the main body (10) enclose a plurality of cavities connected in series, and the plurality of sets of the through hole groups (12) One-to-one correspondence with a plurality of the cavities is performed to form a plurality of resonant cavities (30) having different attenuation frequencies.
  3. 根据权利要求1所述的压力脉动衰减装置，其特征在于，所述外壳(20)与所述主体(10)围设形成多个相互隔离的空腔，多组所述通孔组(12)与多个所述空腔一一对应地连通以形成多种衰减频率不同的共振腔(30)。The pressure pulsation dampening device according to claim 1, wherein the outer casing (20) and the main body (10) enclose a plurality of mutually isolated cavities, and the plurality of sets of the through hole groups (12) One-to-one correspondence with a plurality of the cavities is performed to form a plurality of resonant cavities (30) having different attenuation frequencies.
  4. 根据权利要求1所述的压力脉动衰减装置，其特征在于，各所述通孔组(12)均包括多个通孔，所述多个通孔沿所述主体(10)的周向阵列布置，所述外壳(20)为环形外壳，所述环形外壳套设在所述主体(10)上。The pressure pulsation dampening device according to claim 1, wherein each of said through hole groups (12) each includes a plurality of through holes arranged along a circumferential array of said main body (10) The outer casing (20) is an annular outer casing, and the annular outer casing is sleeved on the main body (10).
  5. 根据权利要求2或3所述的压力脉动衰减装置，其特征在于，所述共振腔(30)的固有频率f r、所述流体通道(11)内的流体介质声速C 0、所述主体(10)的壁厚L、所述通孔组(12)的各个通孔的半径a、所述主体(10)的长度D、穿孔率P满足如下公式：
    Figure PCTCN2018120369-appb-100001
    The pressure pulsation dampening device according to claim 2 or 3, characterized in that the natural frequency f r of the resonant cavity (30), the fluid medium acoustic velocity C 0 in the fluid passage (11), the main body ( The wall thickness L of 10), the radius a of each of the through holes of the through hole group (12), the length D of the main body (10), and the perforation rate P satisfy the following formula:
    Figure PCTCN2018120369-appb-100001
  6. 根据权利要求1所述的压力脉动衰减装置，其特征在于，各组所述通孔组的穿孔率P不同。The pressure pulsation dampening device according to claim 1, wherein each of said sets of said through holes has a different perforation rate P.
  7. 根据权利要求1至4中任一项所述的压力脉动衰减装置，其特征在于，所述外壳(20)上设置有泄油结构(21)。The pressure pulsation dampening device according to any one of claims 1 to 4, characterized in that the outer casing (20) is provided with an oil draining structure (21).
  8. 根据权利要求7所述的压力脉动衰减装置，其特征在于，所述泄油结构(21)为泄油孔。The pressure pulsation dampening device according to claim 7, wherein the oil drain structure (21) is a drain hole.
  9. 根据权利要求8所述的压力脉动衰减装置，其特征在于，所述泄油孔为一个或两个或两个以上。The pressure pulsation dampening device according to claim 8, wherein the oil drain holes are one or two or more.
  10. 一种压缩机，包括压力脉动衰减装置，其特征在于，所述压力脉动衰减装置为权利要求1至9中任一项所述的压力脉动衰减装置。A compressor comprising a pressure pulsation dampening device, wherein the pressure pulsation dampening device is the pressure pulsation dampening device according to any one of claims 1 to 9.
  11. 根据权利要求10所述的压缩机，其特征在于，所述压缩机包括主机(40)和设置在所述主机(40)上的排气腔出口(41)，所述压力脉动衰减装置安装在所述排气腔出口(41)处。The compressor according to claim 10, wherein said compressor comprises a main unit (40) and an exhaust chamber outlet (41) provided on said main unit (40), said pressure pulsation attenuating device being mounted on The exhaust chamber outlet (41).
  12. 根据权利要求10所述的压缩机，其特征在于，所述衰减装置的两端均设置有压力检测元件(50)。The compressor according to claim 10, characterized in that both ends of the damping means are provided with pressure detecting elements (50).
  13. 一种空调器，包括压缩机，其特征在于，所述压缩机为权利要求10至12中任一项所述的压缩机。An air conditioner comprising a compressor, characterized in that the compressor is the compressor according to any one of claims 10 to 12.
PCT/CN2018/120369 2018-02-08 2018-12-11 Pressure pulsation attenuating device, compressor and air conditioner WO2019153871A1 (en)

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Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019005858A1 (en) * 2017-06-28 2019-01-03 3M Innovative Properties Company Microperforated conduit
CN108223383A (en) * 2018-02-08 2018-06-29 珠海格力电器股份有限公司 Pressure fluctuation attenuating device, compressor and air conditioner
CN108980049B (en) * 2018-09-17 2023-09-26 西安交通大学 Air flow pulsation attenuation device of screw compressor
CN112334662B (en) 2018-10-02 2022-08-12 开利公司 Multi-stage resonator for compressor
CN109737066B (en) * 2018-12-29 2019-12-20 烟台菱辰能源有限公司 Air compressor noise eliminator for fuel cell
CN111878405A (en) * 2020-08-19 2020-11-03 珠海格力电器股份有限公司 Air flow pulsation attenuation device capable of reducing noise and screw compressor with same
CN112987508B (en) * 2021-03-04 2022-09-30 长鑫存储技术有限公司 Vibration damping structure and exposure apparatus

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3212603A (en) * 1963-10-24 1965-10-19 Walker Mfg Co Muffler with tuned silencing chambers
CN204100531U (en) * 2014-08-26 2015-01-14 芜湖美智空调设备有限公司 Air-conditioner and silencer thereof
CN205714785U (en) * 2016-04-26 2016-11-23 西安交通大学苏州研究院 A kind of helical-lobe compressor exhaust airstream pulsation dampening and screw compressor system
CN106715849A (en) * 2014-09-09 2017-05-24 3M创新有限公司 Acoustic device
CN207004830U (en) * 2017-06-20 2018-02-13 苏州艾柏特精密机械有限公司 A kind of inverter screw compressor gas attenuator
CN108223383A (en) * 2018-02-08 2018-06-29 珠海格力电器股份有限公司 Pressure fluctuation attenuating device, compressor and air conditioner

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN201972764U (en) * 2011-02-15 2011-09-14 中国航空工业集团公司西安飞机设计研究所 Exhaust muffler utilizing nonlocal reaction acoustic liner principle for auxiliary power unit
CN206111278U (en) * 2016-10-25 2017-04-19 力帆实业(集团)股份有限公司 Car exhaust system premuffler
CN206111279U (en) * 2016-10-25 2017-04-19 力帆实业(集团)股份有限公司 Car premuffler structure
CN208010597U (en) * 2018-02-08 2018-10-26 珠海格力电器股份有限公司 Pressure fluctuation attenuating device, compressor and air conditioner

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3212603A (en) * 1963-10-24 1965-10-19 Walker Mfg Co Muffler with tuned silencing chambers
CN204100531U (en) * 2014-08-26 2015-01-14 芜湖美智空调设备有限公司 Air-conditioner and silencer thereof
CN106715849A (en) * 2014-09-09 2017-05-24 3M创新有限公司 Acoustic device
CN205714785U (en) * 2016-04-26 2016-11-23 西安交通大学苏州研究院 A kind of helical-lobe compressor exhaust airstream pulsation dampening and screw compressor system
CN207004830U (en) * 2017-06-20 2018-02-13 苏州艾柏特精密机械有限公司 A kind of inverter screw compressor gas attenuator
CN108223383A (en) * 2018-02-08 2018-06-29 珠海格力电器股份有限公司 Pressure fluctuation attenuating device, compressor and air conditioner

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