WO2020056982A1 - 具有气流脉动衰减功能的螺杆压缩机滑阀及螺杆压缩机 - Google Patents

具有气流脉动衰减功能的螺杆压缩机滑阀及螺杆压缩机 Download PDF

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Publication number
WO2020056982A1
WO2020056982A1 PCT/CN2018/124061 CN2018124061W WO2020056982A1 WO 2020056982 A1 WO2020056982 A1 WO 2020056982A1 CN 2018124061 W CN2018124061 W CN 2018124061W WO 2020056982 A1 WO2020056982 A1 WO 2020056982A1
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Prior art keywords
screw compressor
exhaust
valve
internal
valve body
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PCT/CN2018/124061
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English (en)
French (fr)
Inventor
邢子文
周明龙
陈文卿
王闯
何志龙
Original Assignee
西安交通大学
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Priority claimed from CN201811083748.7A external-priority patent/CN109058115B/zh
Priority claimed from CN201821518847.9U external-priority patent/CN208996965U/zh
Application filed by 西安交通大学 filed Critical 西安交通大学
Priority to US17/277,288 priority Critical patent/US11920594B2/en
Publication of WO2020056982A1 publication Critical patent/WO2020056982A1/zh

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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
    • 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
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F04C28/12—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves
    • 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
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
    • F16K3/22—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution
    • F16K3/24—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution with cylindrical valve members
    • F16K3/26—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution with cylindrical valve members with fluid passages in the valve member
    • 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
    • F04C2250/00—Geometry
    • F04C2250/10—Geometry of the inlet or outlet
    • F04C2250/102—Geometry of the inlet or outlet of the outlet

Definitions

  • the invention belongs to the technical field of fluid machinery vibration reduction and noise reduction, and relates to a screw compressor slide valve with an air flow pulsation attenuation function.
  • screw compressors As a general-purpose equipment for increasing gas pressure and conveying gas, screw compressors have been widely used in oil, natural gas, chemical, metallurgy and other fields.
  • the screw compressor is a rotary volumetric compressor. Under the drive of a motor, the male and female rotors mesh with each other and rotate synchronously to form a periodic change in the volume of the working chamber, thereby realizing the working process of suction, compression and exhaust.
  • Periodic suction and exhaust of screw compressors will cause periodic fluctuations in gas pressure and flow in the exhaust chamber, resulting in air flow pulsation. Airflow pulsation of a screw compressor will not only reduce the volumetric efficiency of the screw compressor, increase the power consumption of the screw compressor, but also induce vibration noise.
  • Patent US8459963B2 discloses a screw compressor airflow pulsation attenuation device.
  • the internal cavity of the slide valve is designed as an airflow pulsation attenuation cavity.
  • the resonance frequency of the attenuation cavity is adjusted by the diameter, depth and number of perforations to attenuate the compressor exhaust airflow. Purpose of pulsation.
  • the screw compressor needs to be sprayed with a small amount of lubricating medium such as lubricating oil or water to lubricate, the lubricating medium enters the attenuation chamber together with the compressor exhaust gas.
  • the effective attenuation volume of the attenuation cavity changes, the attenuation frequency shifts, and the attenuation effect of the airflow pulsation decreases.
  • the lubricating medium continues to increase.
  • the accumulated lubricating medium height is higher than the lowest position of the axial perforation of the spool valve, the lubricating medium will be discharged from the attenuation chamber to the exhaust chamber through the perforation. , Will affect the effective cross-sectional area of the perforation, and will eventually affect the resonance frequency of the attenuation cavity, resulting in a reduction in the attenuation of the airflow pulsation.
  • the invention aims to solve the problem of air flow pulsation in the exhaust process of a screw compressor from the source, and provides a screw compressor slide valve and a screw compressor with air flow pulsation attenuation function, which can suppress the exhaust air flow pulsation of the screw compressor and reduce Vibration noise induced by air pulsation.
  • the present invention adopts the following technical solutions:
  • a screw compressor spool valve with airflow pulsation attenuation function includes a valve body, and the valve body includes a valve body in a circumferential direction for forming a seal with a screw compressor body, a male rotor, and a female rotor, respectively.
  • the valve body includes a valve body in a circumferential direction for forming a seal with a screw compressor body, a male rotor, and a female rotor, respectively.
  • two or more internal through holes extending toward the valve body suction side end surface are provided on the exhaust side end face of the valve body, and any one of the internal through holes communicates with one or more other internal through holes.
  • a screw compressor with airflow pulsation attenuation function includes a body, an intermeshing male rotor and a female rotor provided in the body, and a slide valve for controlling exhaust.
  • the slide valve includes a valve body, and the valve body.
  • the valve body includes a plurality of wall surfaces in the circumferential direction of the valve body for forming sealing and mating surfaces with the body, the male rotor, and the female rotor, respectively.
  • the exhaust side end surface of the valve body is provided with two or more extending toward the valve body suction side end surface. Internal vias of which any one of the internal vias is in communication with more than one other internal via.
  • the cross-sectional shape of the internal through hole is circular, rectangular, or oval.
  • the internal through-holes are connected through a through-hole communication groove provided on the end face of the valve body on the suction side, and the internal flow passage of the slide valve is formed by the through-hole communication groove and two internal through-holes connected through the through-hole communication groove.
  • the length of the internal flow channel is an odd multiple of the 1/2 wavelength length corresponding to the pulsation frequency of the airflow to be attenuated by the screw compressor.
  • a threaded hole is provided on the suction side end face of the valve body, a hydraulic plug is provided on the threaded hole, and the opening of the internal through hole located on the suction side end face of the valve body and the through hole communication groove are sealed by the hydraulic plug.
  • the threaded hole is provided on the suction side end face of the valve body, a hydraulic plug is provided on the threaded hole, and the opening of the internal through hole located on the suction side end face of the valve body and the through hole communication groove are sealed by the hydraulic plug.
  • the slide valve further includes an axially movable slide valve connecting rod connected to the valve body (the exhaust-side end surface).
  • the invention is based on the principle of sonic interference. While the exhaust of the screw compressor is directly discharged from the exhaust orifice into the exhaust cavity to form a mainstream passage, the exhaust can be formed from the exhaust orifice through the internal through hole of the slide valve. The airflow channel is discharged into the exhaust cavity after a delay to form a side branch flow channel. The difference between the length of the side branch flow channel and the length of the main flow channel can be used to attenuate the air compressor pulsation of the screw compressor.
  • the damping effect of the air flow pulsation in the present invention is only related to the depth of the through hole in the slide valve, which solves the influence of the content of the lubricating medium in the exhaust gas on the damping effect of the air flow pulsation, and has a simple structure, low pressure loss and strong manufacturing and installation operability. And other characteristics, can achieve effective vibration and noise reduction for screw compressors.
  • the present invention changes the time difference between the air flow pulsation and the main flow pulsation in the side flow by optimizing the length difference between the length of the side flow and the length of the main flow, so that the time difference between the two is a half cycle of the air flow pulse to be attenuated, that is The phase difference is 180 degrees, so that the air flow pulsations in the two flow channels cancel each other due to the opposite phases, and the effect of damping the air flow pulsation of the screw compressor is improved.
  • FIG. 1 is a schematic diagram of a three-dimensional structure of a screw compressor in an embodiment of the present invention
  • FIG. 2 is a schematic diagram of the present invention; wherein: (a) pulsations of airflow in each flow channel before attenuation; (b) pulsations of airflow in exhaust cavity after attenuation;
  • FIG. 3 is a schematic diagram of a three-dimensional structure of a screw compressor spool valve (an exhaust side branch flow passage) according to an embodiment of the present invention
  • FIG. 4 is a partial sectional view of a screw compressor spool valve shown in FIG. 3;
  • FIG. 5 is a schematic diagram of a three-dimensional structure of a screw compressor spool valve (a plurality of exhaust side branches) in an embodiment of the present invention
  • FIG. 6 is a partial cross-sectional view of the screw compressor spool valve shown in FIG. 5;
  • FIG. 7 is a schematic view of an exhaust runner of a screw compressor according to an embodiment of the present invention.
  • the screw compressor sucks gas from the suction port 1 of the suction section, and then enters the suction cavity of the body 2 through the gap between the compressor body 2 and the motor stator 3 and the gap between the motor stator 3 and the electronic rotor 4. Compressed to the exhaust section under the meshing action of the male rotor 5 and the female rotor 6, and then enters the exhaust chamber through the exhaust bearing seat 7 from the exhaust orifice, and is then discharged into the exhaust oil sub-tank 9 through the exhaust pipe 8. After being separated from the oil and gas by the built-in oil separation filter 10, it is discharged from the exhaust port 11.
  • the axial displacement of the screw compressor spool valve 20 adjusts the exhaust gas volume of the screw compressor.
  • the phenomenon of airflow pulsation of the screw compressor exhaust is determined by its working principle. It is difficult to reduce the airflow pulsation during the meshing of the female and male rotors of the screw compressor. Therefore, it is the best choice to solve the problem of vibration and noise of screw compressors by attenuating the airflow pulsation from the exhaust source (exhaust orifice) during the exhaustion of the screw compressor and controlling the vibration and noise of the screw compressor induced by the airflow pulsation.
  • the present invention utilizes a slide valve located on the exhaust port of a screw compressor to attenuate the airflow pulsation, and attenuates the airflow pulsation of the screw compressor to the greatest extent from the source, thereby improving the vibration noise of the screw compressor.
  • the screw compressor slide valve proposed by the present invention takes into consideration the periodic characteristics of the screw compressor exhaust air pulsation, and fully considers the installation space of the equipment. Based on the basic principle of acoustic interference, Structural design, between the exhaust port and the exhaust cavity, different lengths of exhaust main flow channels and exhaust side flow channels are formed. The opposite-phase air flow pulsations in the two flow channels are superimposed to cancel each other, thereby maximizing the attenuation of the screw compressor. Air pulsation.
  • the length of the exhaust main passage is short and the exhaust side branch passage is long, a part of the gas having a certain air flow pulsation (that is, pressure fluctuation) controlled by the screw compressor spool valve reaches a part of the exhaust main passage first.
  • the other part is delayed to reach the exhaust cavity through the side branch of the exhaust gas.
  • the pulsation of the airflow lags behind the gas arriving through the exhaust main channel in phase. .
  • the side branch flow pulsation When the gas pulsation of the gas reaching the exhaust cavity via the side branch of the exhaust gas (referred to as the side branch flow pulsation for short) lags the 180 degree phase of the gas flow pulsation of the gas reaching the exhaust cavity through the main flow of the exhaust channel (referred to as the main channel flow pulsation) In the exhaust chamber, the gases from the two flow channels cancel each other due to the opposite phase of the airflow pulsation, so as to achieve the purpose of actively attenuating the airflow pulsation of the screw compressor.
  • the gas flow pulsating phase of the gas reaching the exhaust cavity through the exhaust main passage can reach an odd multiple of 180 degrees.
  • the gas flow pulsation phase is opposite to cancel each other, so as to achieve the purpose of damping the air flow pulsation of the screw compressor.
  • the length difference between the exhaust main channel and the exhaust side branch channel can be determined according to the frequency of airflow pulsation, as follows:
  • f 1 is the fundamental frequency of airflow pulsation of the screw compressor
  • m is the number of teeth of the screw rotor of the screw compressor, which is related to the profile of the screw compressor
  • n is the rotation speed of the screw rotor of the screw compressor.
  • the length difference L between the exhaust side branch channel and the exhaust main channel can be calculated by equation (3):
  • c is the sound velocity of the fluid medium
  • ⁇ t is the time difference between the pulsation of the side stream and the pulsation of the main stream.
  • the screw compressor slide valve includes a valve body and a slide valve connecting rod 22 connected to the valve body, where the valve body includes a wall surface of the body 2 and a male rotor 5 respectively. And the female rotor 6 form a plurality of sealed wall surfaces, which are located in the circumferential direction of the valve body and constitute the slide valve wall surface 21, the valve body is connected to the external drive mechanism through the slide valve connecting rod 22, and the screw compression is adjusted by axial movement Machine exhaust gas volume.
  • the screw compressor slide valve further includes a slide valve through hole 24 for damping the air flow pulsation generated during the exhaust process of the screw compressor.
  • the slide valve through hole 24 includes a pair of openings on the end face of the valve body exhaust side and extending to the suction side.
  • a threaded hole is provided on the suction-side end surface of the valve body (to facilitate through-hole communication Processing of the groove 25), the intake side threaded hole of the valve body is sealed with an internal hexagonal slide valve hydraulic plug 23, so that the slide valve through hole 24 and the through hole communication groove 25 form an exhaust side branch passage 32 (also avoid opening The resulting exhaust gas leaks from the exhaust side to the intake side).
  • the exhaust of the screw compressor with a certain airflow pulsation, part of the exhaust is directly discharged from the exhaust orifice through the exhaust bearing seat 7 into the exhaust cavity to form the exhaust main passage 31, and the other part passes from the exhaust orifice through the exhaust side branch Channel 32 is delayed (refers to entering the valve body from one internal through hole constituting the slide valve through hole 24, and returning to the exhaust side of the valve body from the other internal through hole constituting the slide valve through hole 24, and then flows to the exhaust chamber According to the specific position of the exhaust orifice and the slide valve, the fluid will preferentially flow from the internal through-hole near the higher pressure of the exhaust orifice and flow out from the other internal through-hole) into the exhaust chamber.
  • the gas pulsation phase of the gas in the side branch passage 32 of the exhaust gas lags the phase of the gas pulsation in the exhaust main passage 31.
  • the phase of the gas pulsation in the side branch passage 32 of the exhaust gas is delayed,
  • the pulsation phase of the air flow in the rear exhaust main channel 31 is 180 degrees, the air flow pulsations in the two flow channels are attenuated and cancelled each other due to the opposite phases, thereby attenuating the air flow pulsation of the screw compressor and reducing the vibration noise of the screw compressor.
  • the screw compressor slide valve of the present invention avoids the influence of the content of the lubricating medium in the exhaust gas on the attenuation frequency of the airflow pulsation, thereby solving the content of the lubricating medium in the exhaust gas. Effect on the attenuation effect of air flow pulsation of screw compressor.
  • the screw compressor determines the length difference between the exhaust main flow path 31 and the exhaust side branch flow path 32, so that the air flow pulsation in the two flow paths generates a 180-degree phase difference in the exhaust cavity, which attenuates each other due to the opposite phases.
  • Cancel attenuate the exhaust gas pulsation of the screw compressor from the exhaust source, and reduce the vibration noise of the screw compressor. Because the sound wave is transmitted in a specific periodicity, when the airflow pulsation in the side branch flow path 32 lags behind the airflow pulsation in the main flow path 31 by an odd multiple of 180 degrees, the airflow pulsations in the two flow paths can also cancel each other due to the opposite phases.
  • the screw compressor spool valve 20 can effectively attenuate the fundamental frequency of the airflow pulsation and its odd multiples.
  • designing an exhaust side branch channel 32 can effectively attenuate the fundamental frequency of the airflow pulsation and its odd multiples (ie, 1x, 3x, 5x ).
  • the flow rate of the bypass branch passage 32 can be increased (for example, by increasing the number of slide valve through holes 24 to increase the exhaust Number of by-pass branches 32), and change the length difference between the increased exhaust by-pass channels 32 and the exhaust main passage 31 (for example, by changing the slot depth of the through-hole communication groove 25 to change the by-pass branches 32
  • the difference from the length of the exhaust main flow path 31 is to attenuate the air-wave pulsation by 2 octave and its odd octave (for example, 2 octave, 6 octave, 10 octave ). Therefore, by optimizing the number and length of the exhaust side branch passages 32, the airflow pulsation of the screw compressor base frequency and its odd multiples and 2 times and its odd multiples can be eliminated at the same time.
  • the screw compressor spool valve proposed by the present invention is a damping of airflow pulsation generated during exhaustion of the screw compressor from the source, thereby suppressing vibration excitation caused by airflow pulsation and reducing aerodynamic noise induced by airflow pulsation. Noise reduction device.
  • the screw compressor After the screw compressor goes through the suction process and compression process, it starts the exhaust process.
  • the compressed gas is discharged from the exhaust port. Part of the exhaust gas is directly discharged into the exhaust cavity from the exhaust main passage 31 through the exhaust bearing seat 7; the other part is exhausted into the exhaust cavity after being exhausted from the exhaust side branch passage 32 formed through the internal hole of the slide valve. Because there is a path difference between the exhaust main flow path 31 and the exhaust side branch flow path 32, then there must be a time difference.
  • the path difference between the length of the exhaust main flow path 31 and the exhaust side branch flow path 32 is half of the pulsation frequency of the airflow to be attenuated During the cycle (that is, the phase difference is 180 degrees), because the phases are opposite, the airflows in the two flow channels overlap each other when they converge, and they attenuate the amplitude of the airflow pulsations and cancel each other out. the goal of.
  • the screw compressor spool valve of the present invention can attenuate the air pulse of the screw compressor from the exhaust source of the screw compressor.
  • the screw compressor exhaust system and the air compressor induced by the air pulse are reduced.
  • the piping system has a level of vibration and noise, and has a simple structure, small space volume, small pressure loss, strong operability in manufacturing and installation, and good vibration and noise reduction effects.

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Abstract

一种具有气流脉动衰减功能的螺杆压缩机滑阀（20）及螺杆压缩机，该滑阀（20）主要由壁面（21）和滑阀通孔（24）组成。螺杆压缩机的排气一方面从排气孔口直接排放到排气腔内形成主流道（31），另一方面从排气孔口经过滑阀通孔（24）气流通道延后排放到排气腔内形成旁支流道（32）。由于滑阀（20）内气流通道较长，当旁支流道（32）内气流脉动相位滞后主流道（31）相位180度时，两条流道内的气流脉动因相位相反而相互抵消，衰减螺杆压缩机的气流脉动，抑制压缩机排气气流脉动诱发的振动噪声。螺杆压缩机滑阀（20）的气流脉动衰减效果仅与滑阀（20）内部通孔（24）的深度有关，解决了排气气体中润滑介质含量对气流脉动衰减效果的影响，具有结构简单，压力损失小，实际应用性强，减振降噪效果好等特点。

Description

具有气流脉动衰减功能的螺杆压缩机滑阀及螺杆压缩机 技术领域
本发明属于流体机械减振降噪技术领域，涉及具有气流脉动衰减功能的螺杆压缩机滑阀。
背景技术
螺杆压缩机作为一种用于提高气体压力和输送气体的通用设备，在石油、天然气、化工、冶金等领域得到了广泛应用。螺杆压缩机是一种回转式容积压缩机，在电机驱动下，阳转子与阴转子相互啮合，同步旋转，形成工作腔的容积周期性变化，从而实现吸气、压缩、排气的工作过程。螺杆压缩机周期性吸、排气会导致排气腔内气体压力和流量的周期性波动，产生气流脉动。螺杆压缩机的气流脉动不仅会降低螺杆压缩机的容积效率，增加螺杆压缩机的功率消耗，而且还会诱发振动噪声。
专利US8459963B2公开了一种螺杆压缩机气流脉动衰减装置，利用滑阀内部腔体设计成气流脉动衰减腔，通过穿孔的直径、深度和数量来调节衰减腔的共振频率，达到衰减压缩机排气气流脉动的目的。该专利中，由于螺杆压缩机在运行过程中需要喷微量的润滑油或者水等润滑介质来润滑，润滑介质便与压缩机排气气体一起进入衰减腔。由于润滑介质的累积，衰减腔的有效衰减体积改变，衰减频率偏移，气流脉动的衰减效果下降。随着时间的推移，润滑介质继续增加，当累积的润滑介质高度高于滑阀轴向穿孔的最低位置时，润滑介质会通过穿孔从衰减腔内排出到排气腔内，由于润滑介质的存在，会影响穿孔的有效截面面积，最终也会影响衰减腔的共振频率，导致气流脉动衰减效果下降。
发明内容
本发明旨在从源头上解决螺杆压缩机排气过程中的气流脉动问题，提供一种具有气流脉动衰减功能的螺杆压缩机滑阀及螺杆压缩机，可以抑制螺杆压缩机排气气流脉动，降低气流脉动诱发的振动噪声。
为达到上述目的，本发明采用了以下技术方案：
一种具有气流脉动衰减功能的螺杆压缩机滑阀，该滑阀包括阀体，所述阀体包括位于阀体的周向上的用于分别与螺杆压缩机的机体、阳转子及阴转子形成密封配合面的多个壁面，阀体的排气侧端面上设置有向阀体吸气侧端面延伸的2个以上的内部通孔，其中任意一个内部通孔与1个以上其他内部通孔相连通。
一种具有气流脉动衰减功能的螺杆压缩机，包括机体、设置于机体内的相互啮合的阳 转子和阴转子以及用于控制排气的滑阀，所述滑阀包括阀体，所述阀体包括位于阀体的周向上的用于分别与机体、阳转子及阴转子形成密封配合面的多个壁面，阀体的排气侧端面上设置有向阀体吸气侧端面延伸的2个以上的内部通孔，其中任意一个内部通孔与1个以上的其他内部通孔相连通。
优选的，所述内部通孔的截面形状为圆形、矩形或椭圆形。
优选的，所述内部通孔通过设置在阀体吸气侧端面上的通孔连通槽相连，由通孔连通槽及经该通孔连通槽相连的两个内部通孔构成滑阀内部流道，该内部流道的长度为螺杆压缩机待衰减气流脉动频率所对应1/2波长长度的奇数倍。
优选的，所述阀体的吸气侧端面上设置有螺纹孔，螺纹孔上设置有液压堵头，内部通孔位于阀体吸气侧端面上的开口以及通孔连通槽通过液压堵头密封在螺纹孔内。
优选的，所述滑阀还包括与阀体(排气侧端面)相连的可轴向移动的滑阀连杆。
本发明的有益效果体现在：
本发明基于声波干涉原理，在螺杆压缩机的排气从排气孔口直接排放到排气腔内形成主流道的同时，使排气可以从排气孔口经过滑阀内部通孔所形成的气流通道延后排放到排气腔内形成旁支流道，利用旁支流道长度与主流道长度的长度差，可以达到衰减螺杆压缩机气流脉动的目的。本发明中气流脉动衰减效果仅与滑阀内部通孔的深度有关，解决了排气气体中润滑介质含量对气流脉动衰减效果的影响，而且具有结构简单、压力损失少和制造安装可操作性强等特点，可以对螺杆压缩机达到有效的减振降噪。
进一步的，本发明通过优化旁支流道长度与主流道长度的长度差来改变旁支流道内气流脉动与主流道气流脉动的时间差，使二者时间差为待衰减气流脉动的半个周期，即二者相位差为180度，从而使两条流道内的气流脉动因相位相反而相互抵消，提高衰减螺杆压缩机气流脉动的效果。
附图说明
图1为本发明实施例中螺杆压缩机的三维结构示意图；
图2为本发明的原理图；其中：(a)衰减前各流道内气流脉动；(b)衰减后排气腔内气流脉动；
图3为本发明实施例中螺杆压缩机滑阀(一个排气旁支流道)的三维结构示意图；
图4为图3所示螺杆压缩机滑阀的局部剖视图；
图5为本发明实施例中螺杆压缩机滑阀(多个排气旁支流道)的三维结构示意图；
图6为图5所示螺杆压缩机滑阀的局部剖视图；
图7为本发明实施例中螺杆压缩机排气流道示意图；
图中：1.吸气口、2.机体、3.电机定子、4.电机转子、5.阳转子、6.阴转子、7.排气轴承座、8.排气管、9.排气油分桶、10.油分滤网、11.排气口、20.压缩机滑阀、21.滑阀壁面、22.滑阀连杆、23.滑阀液压堵头、24.滑阀通孔、25.通孔连通槽、31.排气主流道、32.排气旁支流道。
具体实施方式
下面结合附图和实施例对本发明做进一步详细说明。
参见图1，螺杆压缩机从吸气段吸气口1吸入气体，然后从压缩机机体2与电机定子3间的间隙及电机定子3和电子转子4间的间隙进入机体2的吸气腔，在阳转子5和阴转子6的啮合作用下压缩到排气段，然后从排气孔口经排气轴承座7进入排气腔内，随后经排气管8排放到排气油分桶9内，经内置油分滤网10的油气分离后，从排气口11排出。通过螺杆压缩机滑阀20的轴向移动，调节螺杆压缩机的排气气量。螺杆压缩机排气的气流脉动现象是由其工作原理决定的，很难在螺杆压缩机阴、阳转子啮合过程中消减气流脉动。因此，在螺杆压缩机排气过程中从排气源头(排气孔口)上衰减气流脉动，控制气流脉动诱发的螺杆压缩机振动与噪音，是解决螺杆压缩机振动噪声问题的最佳选择。
本发明利用位于螺杆压缩机的排气孔口上的滑阀进行气流脉动衰减，从源头上最大限度的衰减螺杆压缩机的气流脉动，改善螺杆压缩机的振动噪声。
参见图2，本发明提出的螺杆压缩机滑阀全面考虑螺杆压缩机排气气流脉动的周期性特性，并充分考虑设备安装空间问题，基于声波干涉的基本原理，通过对螺杆压缩机滑阀的结构设计，在排气孔口与排气腔之间形成长度不同的排气主流道和排气旁支流道，两条流道内相位相反的气流脉动相互叠加抵消，从而最大限度的衰减螺杆压缩机的气流脉动。具体的，由于排气主流道长度较短，而排气旁支流道较长，通过螺杆压缩机滑阀控制排出的具有一定气流脉动(即压力波动)的气体，一部分经过排气主流道先到达排气腔，另一部分经过排气旁支流道延后到达排气腔，排气旁支流道内的气体在到达排气腔时，其气流脉动在相位上会滞后于经排气主流道到达的气体。当经排气旁支流道到达排气腔的气体的气流脉动(简称旁支流道气流脉动)滞后经排气主流道到达排气腔的气体的气流脉动(简称主流道气流脉动)180度相位时，在排气腔内来自两条流道的气体因气流脉动相位相反而相互抵消，从而达到主动衰减螺杆压缩机气流脉动的目的。因为声波传递具有周期性，所以当经排气旁支流道到达排气腔的气体的气流脉动滞后经排气主流道到达排气腔的气体的气流脉动相位达180度的奇数倍时，也可使两条流道内的气体在到达排气腔时因气流 脉动相位相反而相互抵消，从而达到相应的衰减螺杆压缩机气流脉动的目的。
所述排气主流道与排气旁支流道的长度差可以根据气流脉动频率确定，具体如下：
螺杆压缩机的气流脉动基频可由式(1)计算：
Figure PCTCN2018124061-appb-000001
其中，f 1为螺杆压缩机的气流脉动基频，m为螺杆压缩机阳转子齿数，与螺杆压缩机型线有关；n为螺杆压缩机阳转子的转速。
螺杆压缩机的气流脉动基频及其倍频f N可由式(2)计算：
f N＝N×f 1，N＝1，2，3……          (2)
排气旁支流道与排气主流道长度差L可由式(3)计算：
Figure PCTCN2018124061-appb-000002
其中，c为流体介质声速，Δt为旁支流道气流脉动与主流道气流脉动的时间差。
当
Figure PCTCN2018124061-appb-000003
即旁支流道气流脉动相位滞后主流道气流脉动相位180度时，主流道气流脉动与旁支流道气流脉动因相位相反而相互抵消，可以衰减螺杆压缩机气流脉动基频f 1。
当L确定时
Figure PCTCN2018124061-appb-000004
由于声波传递具有周期性：
Figure PCTCN2018124061-appb-000005
由(3)和(4)可知：
当M＝1时，f＝f 1；
当M＝2时，f＝f 3；
当M＝3时，f＝f 5；
……
因此，当排气旁支流道与主流道的长度差优化后
Figure PCTCN2018124061-appb-000006
不仅可以主动衰减螺 杆压缩机气流脉动基频，还可以衰减气流脉动基频的奇数倍频。
同理，当
Figure PCTCN2018124061-appb-000007
时，即
Figure PCTCN2018124061-appb-000008
时，不仅可以衰减螺杆压缩机气流脉动2倍频，还可以衰减气流脉动2倍频的奇数倍频。将二者(指
Figure PCTCN2018124061-appb-000009
和
Figure PCTCN2018124061-appb-000010
)结合在一起，可以有效衰减螺杆压缩机的气流脉动，降低螺杆压缩机的振动噪声。
参见图3、图4以及图5、图6和图7，上述螺杆压缩机滑阀包括阀体以及与阀体相连的滑阀连杆22，其中阀体包括分别与机体2壁面、阳转子5及阴转子6形成密封的多个壁面，该多个壁面位于阀体的周向上，构成滑阀壁面21，阀体通过滑阀连杆22与外界驱动机构相连，通过轴向移动来调节螺杆压缩机的排气气量。所述螺杆压缩机滑阀还包括用于衰减螺杆压缩机排气过程中产生的气流脉动的滑阀通孔24，滑阀通孔24包括成对开设在阀体排气侧端面并延伸至吸气侧端面的内部通孔，以及在吸气侧端面开设的连接对应两个内部通孔的通孔连通槽25，所述阀体的吸气侧端面上设置有螺纹孔(可方便通孔连通槽25的加工)，阀体的吸气侧螺纹孔用内六角滑阀液压堵头23密封，使滑阀通孔24及通孔连通槽25形成排气旁支流道32(也避免了开孔导致的排气气体从排气侧向吸气侧泄露)。螺杆压缩机的具有一定气流脉动的排气，一部分从排气孔口直接经排气轴承座7排放到排气腔内形成排气主流道31，另一部分从排气孔口经过排气旁支流道32延后(指从构成滑阀通孔24的一个内部通孔进入阀体，并从构成该滑阀通孔24的另一个内部通孔返回阀体排气侧，然后再流向排气腔，根据排气孔口与滑阀的具体位置，流体会优先从靠近排气孔口压力较高的那个内部通孔流入，从另外一个内部通孔流出)排放到排气腔内。由于滑阀通孔24较长，使排气旁支流道32内气体的气流脉动相位滞后于排气主流道31内气体的气流脉动相位，当排气旁支流道32内气体的气流脉动相位延后排气主流道31气流脉动相位180度时，两条流道内的气流脉动因相位相反而相互衰减抵消，从而衰减螺杆压缩机的气流脉动，降低螺杆压缩机的振动噪声。同时，由于阀体内部开设的通孔和通孔连通槽25可以使排气气体和润滑介质直进直出，不会导致润滑介质在滑阀通孔24内累积，润滑介质流入量与流出量必然相等，占用的等效流道截面积也一样，所以本发明的螺杆压缩机滑阀避免了排气气体中润滑介质含量对气流脉动衰减频率的影响，从而解决了排气气体中润滑介质含量对螺杆压缩机的气流脉动衰减效果的影响。
根据螺杆压缩机的运行工况，确定排气主流道31和排气旁支流道32的长度差，使两条流道内气流脉动在排气腔内产生180度相位差，因相位相反而相互衰减抵消，从排气源 头上衰减螺杆压缩机的排气气流脉动，降低螺杆压缩机的振动噪声。因为声波传递具体周期性，所以当排气旁支流道32内气流脉动滞后排气主流道31内气流脉动180度奇数倍相位时，也可以使两条流道内的气流脉动因相位相反而相互抵消，从而达到衰减气流脉动的目的，因此，螺杆压缩机滑阀20可以有效衰减气流脉动的基频及其奇数倍频。综上所述，设计一个排气旁支流道32，可以有效衰减气流脉动的基频及其奇数倍频(即1倍频、3倍频、5倍频……)。
为了同时衰减螺杆压缩机气流脉动基频及其奇数倍频和二倍频及其奇数倍频，可以增加排气旁支流道32的流量(例如，通过增加滑阀通孔24数量来增加排气旁支流道32的数量)，并改变所增加的排气旁支流道32与排气主流道31的长度差(例如，通过改变通孔连通槽25的开槽深度来改变排气旁支流道32与排气主流道31的长度差)，以衰减气流脉动的2倍频及其奇数倍频(例如，2倍频、6倍频、10倍频……)。因此通过排气旁支流道32的数量和长度的优化，可以同时消除螺杆压缩机基频及其奇数倍频和2倍频及其奇数倍的气流脉动。
本发明的工作原理：
参见图7，本发明提出的螺杆压缩机滑阀是一种从源头上衰减螺杆压缩机排气过程中产生的气流脉动，从而抑制气流脉动引起的振动激励和降低气流脉动诱发的气动噪声的减振降噪装置。
螺杆压缩机经过吸气过程和压缩过程后，开始排气过程。压缩终了的气体从排气孔口排出。排气一部分从排气主流道31直接经排气轴承座7排放到排气腔内；另一部分从滑阀内部通孔形成的排气旁支流道32延后排放到排气腔内。由于排气主流道31与排气旁支流道32存在路程差，那么必然存在时间差，当排气主流道31长度与排气旁支流道32长度间的路程差为待衰减气流脉动频率的半个周期(即相位差相差180度)时，由于相位相反，两流道内气流汇合时相互叠加，并相互衰减气流脉动幅值，彼此抵消，从而达到降低螺杆压缩机排气系统及管路系统振动噪声的目的。
总之，本发明的螺杆压缩机滑阀可以从螺杆压缩机排气源头上衰减螺杆压缩机的气流脉动，通过衰减螺杆压缩机的气流脉动幅值，降低气流脉动诱发的螺杆压缩机排气系统和管路系统的振动噪声水准，且结构简单，空间体积小，压力损失小，制造安装的可操作性强，减振降噪效果好。

Claims (10)

  1. 一种具有气流脉动衰减功能的螺杆压缩机滑阀，其特征在于：该滑阀包括阀体，所述阀体包括位于阀体的周向上的用于分别与螺杆压缩机的机体(2)、阳转子(5)及阴转子(6)形成密封配合面的多个壁面，阀体的排气侧端面上设置有向阀体吸气侧端面延伸的2个以上的内部通孔，其中任意一个内部通孔与1个以上的其他内部通孔相连通。
  2. 根据权利要求1所述的具有气流脉动衰减功能的螺杆压缩机滑阀，其特征在于：所述内部通孔的截面形状为圆形、矩形或椭圆形。
  3. 根据权利要求1所述的具有气流脉动衰减功能的螺杆压缩机滑阀，其特征在于：所述内部通孔通过设置在阀体吸气侧端面上的通孔连通槽(25)相连，由通孔连通槽(25)及经该通孔连通槽(25)相连的两个内部通孔所构成的滑阀内部流道的长度为螺杆压缩机待衰减气流脉动频率所对应1/2波长长度的奇数倍。
  4. 根据权利要求1所述的具有气流脉动衰减功能的螺杆压缩机滑阀，其特征在于：所述阀体的吸气侧端面上设置有螺纹孔，螺纹孔上设置有液压堵头，所述内部通孔位于阀体吸气侧端面上的开口以及通孔连通槽(25)通过液压堵头密封在螺纹孔内。
  5. 根据权利要求1所述的具有气流脉动衰减功能的螺杆压缩机滑阀，其特征在于：所述滑阀还包括与阀体相连的可轴向移动的滑阀连杆(22)。
  6. 一种具有气流脉动衰减功能的螺杆压缩机，其特征在于：包括机体(2)、设置于机体(2)内的相互啮合的阳转子(5)和阴转子(6)以及用于控制排气的滑阀，所述滑阀包括阀体，所述阀体包括位于阀体的周向上的用于分别与机体(2)、阳转子(5)及阴转子(6)形成密封配合面的多个壁面，阀体的排气侧端面上设置有向阀体吸气侧端面延伸的2个以上的内部通孔，其中任意一个内部通孔与1个以上的其他内部通孔相连通。
  7. 根据权利要求6所述的具有气流脉动衰减功能的螺杆压缩机，其特征在于：所述内部通孔的截面形状为圆形、矩形或椭圆形。
  8. 根据权利要求6所述的具有气流脉动衰减功能的螺杆压缩机，其特征在于：所述内部通孔通过设置在阀体吸气侧端面上的通孔连通槽(25)相连，由通孔连通槽(25)及经该通孔连通槽(25)相连的两个内部通孔所构成的滑阀内部流道的长度为螺杆压缩机待衰减气流脉动频率所对应1/2波长长度的奇数倍。
  9. 根据权利要求6所述的具有气流脉动衰减功能的螺杆压缩机，其特征在于：所述阀体的吸气侧端面上设置有螺纹孔，螺纹孔上设置有液压堵头，所述内部通孔位于阀体吸气侧端面上的开口以及通孔连通槽(25)通过液压堵头密封在螺纹孔内。
  10. 根据权利要求6所述的具有气流脉动衰减功能的螺杆压缩机，其特征在于：所述 滑阀还包括与阀体相连的可轴向移动的滑阀连杆(22)。
PCT/CN2018/124061 2018-09-17 2018-12-26 具有气流脉动衰减功能的螺杆压缩机滑阀及螺杆压缩机 WO2020056982A1 (zh)

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