WO2023045767A1 - 振动频率调节系统 - Google Patents

振动频率调节系统 Download PDF

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Publication number
WO2023045767A1
WO2023045767A1 PCT/CN2022/117739 CN2022117739W WO2023045767A1 WO 2023045767 A1 WO2023045767 A1 WO 2023045767A1 CN 2022117739 W CN2022117739 W CN 2022117739W WO 2023045767 A1 WO2023045767 A1 WO 2023045767A1
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WO
WIPO (PCT)
Prior art keywords
vibration
mode
counterweight
type
vibratable
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2022/117739
Other languages
English (en)
French (fr)
Inventor
汤庆华
林坤
马小魁
周朴
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
York Wuxi Air Conditioning and Refrigeration Co Ltd
Johnson Controls Tyco IP Holdings LLP
Original Assignee
York Wuxi Air Conditioning and Refrigeration Co Ltd
Johnson Controls Tyco IP Holdings LLP
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by York Wuxi Air Conditioning and Refrigeration Co Ltd, Johnson Controls Tyco IP Holdings LLP filed Critical York Wuxi Air Conditioning and Refrigeration Co Ltd
Priority to US18/695,787 priority Critical patent/US20240384773A1/en
Priority to EP22871815.1A priority patent/EP4407185A4/en
Priority to KR1020247013835A priority patent/KR20240090244A/ko
Publication of WO2023045767A1 publication Critical patent/WO2023045767A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/28—Safety arrangements; Monitoring
    • 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
    • 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
    • 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
    • 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
    • F04C29/065—Noise dampening volumes, e.g. muffler chambers
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/28—Counterweights, i.e. additional weights counterbalancing inertia forces induced by the reciprocating movement of masses in the system, e.g. of pistons attached to an engine crankshaft; Attaching or mounting same
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F7/00—Vibration-dampers; Shock-absorbers
    • F16F7/10—Vibration-dampers; Shock-absorbers using inertia effect
    • F16F7/1005—Vibration-dampers; Shock-absorbers using inertia effect characterised by active control of the mass
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D19/00—Control of mechanical oscillations, e.g. of amplitude, of frequency, of phase
    • G05D19/02—Control of mechanical oscillations, e.g. of amplitude, of frequency, of phase characterised by the use of electric means
    • 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
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/806—Pipes for fluids; Fittings therefor
    • 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
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/807—Balance weight, counterweight
    • 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
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/81—Sensor, e.g. electronic sensor for control or monitoring
    • 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
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/811—Actuator for control, e.g. pneumatic, hydraulic, electric
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/12—Vibration
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/12—Vibration
    • F04C2270/125—Controlled or regulated
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/80—Diagnostics
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/86—Detection
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2222/00—Special physical effects, e.g. nature of damping effects
    • F16F2222/08—Inertia
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2230/00—Purpose; Design features
    • F16F2230/0011—Balancing, e.g. counterbalancing to produce static balance
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2230/00—Purpose; Design features
    • F16F2230/08—Sensor arrangement
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2230/00—Purpose; Design features
    • F16F2230/18—Control arrangements

Definitions

  • the application relates to a vibration frequency adjustment system, especially a vibration frequency adjustment system for a variable frequency screw unit.
  • variable frequency screw compressor in the variable frequency screw unit discharges gas to the exhaust pipe at a certain frequency.
  • the operating frequency of the variable frequency screw compressor is the same or close to the natural vibration frequency of the exhaust pipe, resonance is likely to occur. It is hoped that the exhaust pipe can be adjusted for vibration isolation to reduce the impact of resonance.
  • the present application provides a vibration frequency adjustment system, which can adjust the natural vibration frequency of the exhaust pipe, so as to reduce the vibration of the exhaust pipe.
  • the vibration frequency adjustment system of the present application includes a vibratory component, at least one counterweight, at least one driving device and a controller.
  • the vibratable component is configured to be connected to a vibration source, the vibration source has an operating frequency range, and the vibratable component has a natural frequency of vibration.
  • the at least one counterweight is configured to be movable along the vibratable member.
  • the at least one drive device is configured to enable the at least one counterweight to be held or moved to different counterweight positions on the vibratable member.
  • the controller is communicatively connected to the at least one drive device.
  • the controller when the vibratable component vibrates, there is at least one maximum vibration displacement position on the vibratable component.
  • the controller is configured such that when the vibratable member vibrates, the controller is capable of controlling the at least one driving device such that the at least one counterweight is held at or moved to deviate from the vibratable The at least one maximum vibration displacement location on the component.
  • the controller is configured to be able to drive the at least one counterweight in the corresponding two preset counterweight positions by controlling the at least one driving device. Switch between counterweight positions.
  • the controller is configured to be able to separately drive each of the at least one counterweight in the at least one counterweight by controlling each of the at least one driving device. Switch between the corresponding two preset counterweight positions in the above counterweight positions.
  • the vibratable component can vibrate in a "C-shape” mode or an "S-shape” mode within the operating frequency range of the vibration source.
  • the counterweight positions include “C-shaped” mode-shaped counterweight positions and "S-shaped” mode-shaped counterweight positions.
  • the controller is configured to be able to control the at least one driving device according to the mode shape of the vibratable part: when the vibratable part vibrates in the "C-shape" mode, the controller controls the said at least one driving device causes said at least one counterweight to be held or moved to said "C-shape" mode weight position; or, when said vibratable member vibrates in said "S-shape” mode , the controller controls the at least one driving device such that the at least one counterweight is held or moved to the "S-shape” modal counterweight position.
  • the vibratable component when the vibratable component vibrates in the "C-type” mode, the vibratable component has a maximum vibration displacement position of the "C-type” mode, and the "C-type"
  • the position of the mode-shape counterweight is separated from the position of the maximum vibration displacement of the "C-type” mode-shape by a certain distance.
  • the vibratable part When the vibratable part vibrates with the "S-type” mode shape, the vibratable part has one "S-type” mode-type minimum vibration displacement position and two "S-type” mode-type maximum vibration displacement positions, so The maximum vibration displacement positions of the two "S-type” vibration modes are respectively the first maximum vibration displacement position of the "S-type” vibration mode and the second maximum vibration displacement position of the "S-type” vibration mode.
  • the heavy position is separated by a certain distance from the maximum vibration displacement positions of the two "S-type” mode shapes.
  • the "C-type” vibration mode counterweight position includes a "C-type” vibration mode first counterweight position and a "C-type” vibration mode second counterweight position.
  • the first counterweight position of the "C-type” vibration shape is located on one side of the maximum vibration displacement position of the "C-type” vibration shape
  • the second counterweight position of the "C-type” vibration shape is located at the "C-type” The opposite side of the position of maximum vibration displacement of the mode shape.
  • the counterweight position of the "S-type” vibration mode is located at the minimum vibration displacement position of the "S-type” vibration mode.
  • the position of the first counterweight of the "C-type” vibration mode is adjacent to the first maximum vibration displacement position of the "S-type” vibration mode
  • the second counterweight of the "C-type” vibration mode The location is adjacent to the position of the second maximum vibrational displacement of the "S-shaped" mode shape.
  • the at least one counterweight is configured to have a predetermined weight, and the predetermined weight of the at least one counterweight is such that: When the "mode shape vibrates, the vibration displacement of the vibratable component at the maximum vibration displacement position of the "C-type” mode shape is less than a predetermined vibration displacement value; and when the vibratable component is in the "S-type” mode shape When vibrating, the vibration displacements of the vibratable component at the maximum vibration displacement positions of the two "S-shaped" mode shapes are both smaller than the predetermined vibration displacement value.
  • the number of the at least one driving device is two, namely the first driving device and the second driving device.
  • the quantity of the at least one counterweight is two, namely a first counterweight and a second counterweight.
  • the controller is configured to: store the natural vibration frequency of the vibratable component, and the natural vibration frequency at least includes the natural vibration frequency of the "C-type” vibration mode and the "S-type” vibration frequency a mode shape natural frequency of vibration; acquiring a current frequency of vibration of a vibratable part; and comparing the current frequency of vibration of the vibratable part with the natural frequency of vibration of the vibratable part.
  • the controller judges that the deviation between the current vibration frequency of the vibratable component and the natural vibration frequency of the “C-type” mode of the vibratable component is less than a preset threshold, the controller judging that the vibratable part vibrates in a "C-type” mode, or when the controller judges that the current vibration frequency of the vibratable part is different from the natural vibration of the "S-type” mode of the vibratable part
  • the controller judges that the vibratable component vibrates in an "S-shape" mode.
  • the method for acquiring the current vibration frequency of the vibratory component includes: (1) the controller receives a signal indicating the operating frequency of the vibration source from the vibration source, and sends the vibration source to The operating frequency of the vibratable component is used as the current vibration frequency; or (2) the vibration frequency adjustment system is configured to include a frequency detecting device for detecting the current vibration frequency of the vibratable component The controller receives a signal indicative of the current vibration frequency of the vibratable member from the frequency detecting device.
  • the vibration frequency adjustment system further includes a detection device for detecting the vibration of the vibratable component, and the detection device is communicatively connected to the controller.
  • the detecting device includes: a first position detecting device, a second position detecting device and a third position detecting device.
  • the first position detection device is arranged at the first detection position of the vibrator part to detect the vibration of the vibrator part at the first detection position, and the first detection position is located in the "C-shaped ” at the position of the maximum vibration displacement of the mode shape.
  • the second position detection device is arranged at the second detection position of the vibrator part to detect the vibration of the vibrator part at the second detection position, and the second detection position is located in the "S-shaped ” at the position of the first maximum vibration displacement of the mode shape.
  • the third position detection device is arranged at the third detection position of the vibrator part to detect the vibration of the vibrator part at the third detection position, and the third detection position is located in the "S-shaped ” at the position of the second maximum vibration displacement of the vibration mode.
  • the first position detection device includes a first sensor in the first direction and a first sensor in the second direction
  • the second position detection device includes a second sensor in the first direction and a second sensor in the second direction
  • the third position detection device includes a third sensor in the first direction and a third sensor in the second direction.
  • the controller is configured to: determine the vibration of the vibratable member in the first direction at the first detection position based on the detection of the first direction first sensor in the first position detection device Displacement Y1; based on the detection of the first sensor in the second direction in the first position detection device, determine the vibration displacement Z1 of the vibratable component in the second direction at the first detection position; based on the The detection of the second sensor in the first direction in the second position detection device determines the vibration displacement Y2 of the vibratory component in the first direction at the second detection position; based on the second The detection of the second sensor in the second direction in the position detection device determines the vibration displacement Z2 of the vibratable member in the second direction at the second detection position; based on the third position detection device The detection of the third sensor in the first direction in the first direction determines the vibration displacement Y3 of the vibratory member in the first direction at the third detection position; and The detection by the third sensor in the second direction determines the vibration displacement Z3 of the vibratable component in the second direction at the third detection position
  • the controller judges: (i) Y2 ⁇ Z2, Y1 ⁇ Z1, Y3 ⁇ Z3, Z1 ⁇ Z2, Z1 ⁇ Z3, and both Z2 and Z3 are greater than the predetermined vibration displacement value, or (ii) Y2 >Z2, Y1>Z1, Y3>Z3, Y1 ⁇ Y2, Y1 ⁇ Y3, and both Y2 and Y3 are greater than the predetermined vibration displacement value, the controller judges that the vibratory component vibrates in the "S shape" type vibrates.
  • the detection device is a unidirectional displacement sensor or a unidirectional acceleration sensor.
  • the at least one counterweight is a ring structure, and a rolling device is provided on the inner side of the ring structure, and the rolling device is a roller or a ball, and the rolling device can rolling on the surface of the vibratory component.
  • the above-mentioned vibration frequency adjustment system is characterized in that: the ring structure is an eccentric ring.
  • the above-mentioned vibration frequency adjustment system is characterized in that three evenly distributed rolling devices are arranged on the inner side of the ring structure.
  • the at least one driving device is a pneumatic or hydraulic actuator
  • the at least one driving device includes a cylinder and a push rod, and one end of the push rod is telescopically fixed on the cylinder In the body, the other end of the push rod is connected to a corresponding one of the at least one counterweight.
  • the vibration source is a variable frequency screw compressor
  • the vibrable component is an exhaust pipe connected to the exhaust port of the variable frequency screw compressor
  • Fig. 1 is a schematic perspective view of the structure of an embodiment of a variable frequency screw unit according to the prior art.
  • 2A-2C show the mode shapes corresponding to different natural vibration frequencies of the exhaust pipe obtained according to the test of the present application.
  • Fig. 3 shows a structural schematic diagram of an embodiment for determining in which formation the exhaust pipe is vibrating according to the present application.
  • 4A to 4C are structural schematic diagrams of an embodiment of a counterweight arrangement according to the present application.
  • 5A to 5B are structural schematic diagrams of another embodiment of the arrangement of counterweights according to the present application.
  • Fig. 6 is a block diagram of a controller according to the present application.
  • Fig. 1 is a schematic perspective view of the structure of a variable frequency screw unit 10 according to the prior art.
  • the variable frequency screw unit 10 includes a variable frequency screw compressor 101 , an exhaust pipe 102 , an evaporator 103 and a condenser 104 .
  • the air inlet of the variable frequency screw compressor 101 is connected to the air outlet of the evaporator 103 .
  • the air inlet of the exhaust pipe 102 is connected with the air outlet of the variable frequency screw compressor 101 , and the air outlet of the air outlet 102 is connected with the condenser 104 .
  • variable frequency screw compressor 101 can compress the gaseous refrigerant from the evaporator 103 and deliver it to the condenser 104 through the exhaust pipe 102 .
  • the variable frequency screw compressor 101 delivers the compressed gaseous refrigerant to the exhaust pipe 102 with the exhaust pulsation frequency within a certain range.
  • the exhaust pulsation frequency of the variable frequency screw compressor 101 reaches or approaches the natural vibration frequency of the exhaust pipeline 102, the exhaust pipeline 102 generates resonance.
  • the exhaust pipe 102 resonates, the vibration amplitude and stress strain of the exhaust pipe 102 are very large, which will reduce the service life of the exhaust pipe 102 .
  • the vibration of the exhaust pipe 102 will drive the vibration of the variable frequency screw compressor 101, the evaporator 103, the condenser 104 and the parts arranged on these devices, the excessive vibration of the exhaust pipe 102 will also affect the frequency conversion screw unit 10. of normal operation. In addition, the excessive vibration generated when the exhaust duct 102 resonates will also cause noise problems.
  • the present application places weights at selected weight locations on the exhaust duct 102 .
  • the position of the counterweight selected in this application is at a certain distance from the maximum vibration displacement position of the exhaust duct 102 .
  • the present application controls the different counterweight positions of the counterweight on the exhaust duct 102 according to the current vibration condition of the exhaust duct 102 , so that the mass distribution and stiffness of the exhaust duct 102 can be maintained or changed as required.
  • the present application can maintain or change the natural vibration frequency of the exhaust pipe 102 according to the current vibration situation of the exhaust pipe 102 according to actual needs, so as to ensure the exhaust pulsation frequency of the variable frequency screw compressor 101 and the natural vibration frequency of the exhaust pipe 102 The difference is large enough, so that the vibration of the exhaust pipe 102 is small enough, so as not to cause adverse effects on the operation of the exhaust pipe 102 and the variable frequency screw unit 10 .
  • the present application can determine in which vibration mode the exhaust pipeline 102 is vibrating when the variable frequency screw compressor 101 is exhausting the exhaust pipeline 102, and based on this, the counterweight remains or moves to The corresponding counterweight position on the exhaust pipe 102 .
  • the mode shape in which the exhaust duct 102 is vibrating can be determined in a number of ways. An example embodiment of determining in which vibration mode the exhaust duct 102 is vibrating is discussed in detail in conjunction with FIGS. 2A to 3 .
  • the exhaust duct 102 is tested in advance to obtain the The corresponding mode shape at the natural frequency of vibration.
  • the vibration displacement at multiple positions when the exhaust pipe 102 vibrates is detected in real time to judge the exhaust gas. In what mode the pipe 102 is vibrating.
  • the simulation analysis method (for example, according to the Chinese national standard GB/T33582-2017 "General Rules for Mechanical Product Structure Finite Element Mechanical Analysis”) can be pre-tested to obtain the corresponding mode shape of the exhaust pipe 102 at the natural vibration frequency.
  • the exhaust pulsation frequency of the variable frequency screw compressor 101 is in the range of 80-250 Hz.
  • the inventors of the present application have found through tests that the exhaust pipe 102 has three natural vibration frequencies in the frequency range of 80-250 Hz. When the actual vibration frequency of the exhaust pipe 102 reaches or approaches these three natural vibration frequencies, the exhaust The pipeline 102 vibrates in three corresponding modes. These three mode shapes of the exhaust duct 102 are schematically shown in FIGS. 2A-2C .
  • FIG. 2A shows the "C-shape" mode shape of the exhaust duct 102 .
  • the exhaust pipe 102 has a "C-type” vibration in the Y-axis direction (the height direction of the exhaust pipe 102), and has a "C-type” vibration at position 201. type maximum vibration displacement.
  • FIG. 2B shows a first “S-shaped” mode shape of the exhaust duct 102 .
  • the exhaust pipe 102 vibrates in the Z-axis direction (direction perpendicular to the length and height of the exhaust pipe 102), and in the position Positions 212 and 213 have the maximum vibration displacement of the first "S-type” mode shape, and position 211 has the minimum vibration displacement of the first "S-type” mode mode.
  • FIG. 2C shows a second “S-shaped” mode shape of the exhaust duct 102 .
  • the exhaust duct 102 vibrates in an "S-shaped” direction in the Y-axis direction (the height direction of the duct), and has a second "S-shaped” vibration at positions 222 and 223.
  • the maximum vibration displacement position 201 of the "C-type” mode shape of the exhaust pipe 102, the minimum vibration displacement position 211 of the first "S-type” mode shape, and the minimum vibration displacement position 221 of the second "S-type” mode shape roughly coincide, and the exhaust pipe
  • the minimum vibration displacement position 211 of the first "S-type” mode of 102 and the minimum vibration displacement position 221 of the second "S-type” mode approximately coincide, and the maximum vibration displacement position 212 of the first "S-type” mode of the exhaust pipe 102
  • the maximum vibration displacement position 222 of the second "S-type” mode approximately coincides with the maximum vibration displacement position 213 of the first "S-type” mode and the maximum vibration displacement position 223 of the second "S-type” mode approximately coincides.
  • the mode shape detection results for the exhaust duct 102 are stored in the controller (shown in FIG. 3 ).
  • Fig. 3 shows a structural schematic diagram of an embodiment for determining in real time in which formation the exhaust pipeline 102 is vibrating during the process of the variable frequency screw compressor 101 exhausting the exhaust pipeline 102.
  • it is determined in which formation the exhaust duct 102 is vibrating by detecting the vibration displacement of the exhaust duct 102 at different positions.
  • three detection positions 311 , 312 , 313 are set on the exhaust pipe 102 .
  • the first detection position 311 is set at the maximum vibration displacement position 201 of the "C type” mode shape
  • the second detection position 312 is set at the maximum vibration displacement position 212 of the first "S type” mode shape (that is, the second "S type” At the maximum vibration displacement position 222)
  • the third detection position 313 is set at the maximum vibration displacement position 213 of the first "S-shaped” mode shape (that is, the maximum vibration displacement position 223 of the second "S-shaped” mode shape).
  • the first position detection device includes a first sensor 301 in a first direction and a first sensor 302 in a second direction, and the first sensor 301 in a first direction is used to detect the vibration of the exhaust pipe 102 in the Y-axis direction at the first detection position 311 , the first sensor 302 in the second direction is used to detect the vibration of the exhaust pipe 102 in the Z-axis direction at the first detection position 311 .
  • a second position detection device is arranged at the second detection position 312 .
  • the second position detection device includes a second sensor 303 in the first direction and a second sensor 304 in the second direction, the second sensor 303 in the first direction is used to detect the vibration of the exhaust pipe 102 in the Y-axis direction at the second detection position 312 , the second sensor 304 in the second direction is used to detect the vibration of the exhaust pipe 102 in the Z-axis direction at the second detection position 312 .
  • a third position detection device is provided at the third detection position 313 .
  • the third position detection device includes a third sensor 305 in the first direction and a third sensor 306 in the second direction, the third sensor 305 in the first direction is used to detect the vibration of the exhaust pipe 102 in the Y-axis direction at the third detection position 313 , the third sensor 306 in the second direction is used to detect the vibration of the exhaust pipe 102 in the Z-axis direction at the third detection position 313 .
  • the variable frequency screw unit 10 also includes a controller 307, which is connected to the sensors 301, 302, 303, 304, 305, 306 in communication, so that the A signal indicative of a vibration condition of the exhaust duct 102 at a corresponding detected location is received.
  • the controller 307 determines the vibration displacement of the exhaust pipe 102 at these positions according to the received signals indicating the vibration of the exhaust pipe 102 at the three detection positions 311, 312, 313, and then determines that the exhaust pipe 102 is moving at Which mode of vibration occurs.
  • the controller 307 determines the vibration displacement Y1 of the exhaust pipe 102 in the Y-axis direction at the first detection position 311 based on the signal received from the first sensor 301 in the first direction.
  • the signal received by the sensor 302 is used to determine the vibration displacement Z1 of the exhaust pipe 102 in the Z-axis direction at the first detection position 311. Based on the signal received from the second sensor 303 in the first direction, it is determined that the exhaust pipe 102 Second, the vibration displacement Y2 of the detection position 312 in the Y-axis direction, based on the signal received from the second sensor 304 in the second direction, determine the vibration displacement Z2 of the exhaust pipe 102 in the Z-axis direction at the second detection position 312 , based on the signal received from the third sensor 305 in the first direction, determine the vibration displacement Y3 of the exhaust pipe 102 in the Y-axis direction at the third detection position 313, based on the signal received from the third sensor 306 in the second direction , to determine the vibration displacement Z3 of the exhaust pipe 102 in the Z-axis direction at the third detection position 313 .
  • the controller 307 compares the vibration displacements of the exhaust duct 102 at the three detection locations 311 , 312 , 313 to determine in which vibration mode the exhaust duct 102 is vibrating. When the controller 307 judges that Z2 ⁇ Y2, Z1 ⁇ Y1, Z3 ⁇ Y3, and both Y2 and Y3 are smaller than the predetermined vibration displacement value, and Y1 is greater than the predetermined vibration displacement value, the controller 307 judges that the exhaust pipe 102 is Vibration occurs in the "C-type" mode.
  • the controller 307 judges that the exhaust pipe 102 is moving at the first "S Type” vibration occurs.
  • the controller 307 judges that Y2>Z2, Y1>Z1, Y3>Z3, Y1 ⁇ Y2, Y1 ⁇ Y3, and both Y2 and Y3 are greater than the predetermined vibration displacement value
  • the controller 307 judges that the exhaust pipe 102 is moving at the second "S Type” vibration occurs.
  • the predetermined vibration displacement value is set so that when the vibration displacement does not exceed this value, no damage will be caused to the exhaust pipe 102 and the variable frequency screw unit 10 .
  • the predetermined vibration displacement value is set to 60 ⁇ m.
  • the sensors 301, 302, 303, 304, 305, and 306 can all be unidirectional acceleration sensors, which are used to detect the motion acceleration of the exhaust pipe 102 in the Y-axis and Z-axis directions at each detection position, and send them to the controller 307. Signal indicating detected motion acceleration.
  • the controller 307 can calculate the vibration displacement of the exhaust pipe 102 at each detection position based on the acceleration signals from these unidirectional acceleration sensors.
  • the sensors 301, 302, 303, 304, 305, and 306 can also be all unidirectional displacement sensors, which are used to detect the vibration displacement of the exhaust pipe 102 in the Y-axis and Z-axis directions at each detection position, and report to the controller 307 A signal indicative of the detected vibration displacement is sent.
  • the exhaust pipe 102 that has been installed in the specific variable frequency screw unit 10 can be tested in advance by using the test modal method to determine its natural vibration frequency and its corresponding mode shape.
  • the test modal method determines its natural vibration frequency and its corresponding mode shape.
  • the exhaust pipe 102 also has three natural vibration frequencies and three vibration frequencies as shown in Figures 2A to 2C. Corresponding mode shape.
  • the test results are stored in the controller 307 .
  • the controller 307 determines in real time the current vibration frequency of the exhaust pipe 102 when vibration occurs. For example, the controller 307 may receive a signal indicating the discharge pulsation frequency of the variable frequency screw compressor 101 from the variable frequency screw compressor 101 , and use the discharge pulsation frequency of the variable frequency screw compressor 101 as the current vibration frequency of the exhaust pipe 102 . For another example, the controller 307 may also receive a signal indicating the vibration of the exhaust pipe 102 from the frequency detection device of the exhaust pipe 102 , and perform spectrum analysis based on the signal to determine the current vibration frequency of the exhaust pipe 102 .
  • the frequency detecting device may be six unidirectional acceleration sensors or unidirectional displacement sensors as shown in FIG. 3 , or It may be three three-way acceleration sensors or three-way displacement sensors arranged at any three positions of the exhaust pipe 102 .
  • the controller 307 determines the current mode shape of the exhaust duct 102 by determining its current vibration frequency, when the current vibration frequency of the exhaust duct 102 corresponds to the "C
  • the controller 307 judges that the exhaust pipe 102 is vibrating in the "Type C” mode.
  • the controller 307 judges that the exhaust Pipe 102 is vibrating in a first "S-shape” mode.
  • the controller 307 judges that the exhaust Pipe 102 is vibrating in a second "S-shape" mode.
  • the preset value of the difference between the current vibration frequency of the exhaust pipe 102 and each natural vibration frequency may be 4 Hz.
  • the controller 307 determines in which vibration mode the exhaust pipe 102 is vibrating, the controller 307 maintains or adjusts the position of the counterweight to maintain or change the natural vibration frequency of the exhaust pipe 102, so as to ensure the vibration of the exhaust pipe 102.
  • the difference between the natural vibration frequency and the exhaust pulsation frequency of the variable frequency screw compressor 101 is large enough, so that the vibration of the exhaust pipeline 102 is small enough to avoid damage to the exhaust pipeline 102 and the variable frequency screw unit 10 . Maintaining or adjusting the position of the counterweights is described in connection with the different embodiments of the counterweight arrangement shown in FIGS. 4A to 4C and FIGS. 5A to 5B .
  • two counterweights 401 and 402 are provided on the exhaust pipe 102 .
  • Two driving devices 407 and 408 are also arranged on the exhaust pipe 102, the driving device 407 is connected with the counterweight 401 for driving the counterweight 401, and the driving device 408 is connected with the counterweight 402 for driving the counterweight 402.
  • the driving device 407 and the driving device 408 are respectively connected in communication with the controller 307 , so that the controller 307 can control the driving devices 407 and 408 to drive the counterweights 401 and 402 .
  • the exhaust pipe 102 is provided with three counterweight positions 421, 422, 423, the controller 307 can control the driving device 407 so that the counterweight 401 moves to the counterweight position 421 or 422, the controller 307 can control the driving device 408 so that the counterweight 402 moves to the counterweight position 421 or 423 .
  • the first counterweight position 421 is set to the maximum vibration displacement position 212, 213 of the first "S-type" mode shape of the exhaust pipe 102 (that is, the second "S-type" mode shape maximum vibration displacement position 222, 223) are separated by a certain distance.
  • the second counterweight position 422 is located on one side of the maximum vibration displacement position 201 of the "C-type” vibration mode, and is separated from the maximum vibration displacement position 201 of the "C-type” mode mode by a certain distance.
  • the third counterweight position 423 is located on the other side of the maximum vibration displacement position 201 of the "C-type” vibration mode, and is separated from the maximum vibration displacement position 201 of the "C-type” mode mode by a certain distance.
  • the first counterweight position 421 is located at or adjacent to the minimum vibration displacement position 211 of the first "S-type” mode shape (that is, the minimum vibration displacement position 221 of the second "S-type” mode mode), and the second The counterweight position 422 is located at or adjacent to the first "S-type” mode shape maximum vibration displacement position 212 (that is, the second "S-type” mode mode maximum vibration displacement position 222), and the third counterweight position 423 is located at or adjacent to the first The maximum vibration displacement position 213 of the first "S-shaped” mode shape (that is, the maximum vibration displacement position 223 of the second "S-shaped” mode shape).
  • the controller 307 determines that the exhaust pipe 102 is vibrating in the "C-type" vibration mode, if the counterweights 401 and 402 are at the first counterweight position 421 at this time, the controller 307 controls the driving device 407 to place the counterweight 401 Move from the first counterweight position 421 to the second counterweight position 422, and control the driving device 408 to move the counterweight 402 from the first counterweight position 421 to the third counterweight position 423; In the second counterweight position 422, and the counterweight 402 is already in the third configuration position 423, the controller 307 controls the driving device 407 to keep the first counterweight 401 at the second counterweight position 422, and controls the driving device 408 to The second counterweight 402 remains in the third counterweight position 423 .
  • the controller 307 determines that the exhaust pipe 102 is vibrating in the first "S-shape" or the second "S-shape” mode, if the counterweight 401 is at the second counterweight position 422 and the counterweight 402 is at the first In the third configuration position 423, the controller 307 controls the driving device 407 to move the first counterweight 401 to the first counterweight position 421, and controls the driving device 408 to move the second counterweight 402 to the first counterweight position 421; If the counterweights 401 and 402 are already in the first counterweight position 421 at this moment, the controller 307 controls the driving device 407 to keep the first counterweight 401 at the first counterweight position 421, and controls the driving device 408 to place the second counterweight The weight 402 also remains in the first counterweight position 421 .
  • the weights 401, 402 are configured to have a predetermined weight.
  • the predetermined weight is such that, when the exhaust duct 102 vibrates in the "C-type” mode, the exhaust duct 102
  • the difference between the natural vibration frequency of the variable frequency screw unit 10 and the exhaust pulsation frequency of the variable frequency screw unit 10 reaches a predetermined frequency difference, and when the exhaust pipe 102 vibrates in the first or second "S-type” mode, the counterweights 401, 402
  • the corresponding counterweight position 421 of the first or second "S-shaped” mode is located, the difference between the natural vibration frequency of the exhaust pipe 102 and the exhaust pulsation frequency of the variable frequency screw unit 10 also reaches the predetermined frequency difference.
  • the vibration displacement of the exhaust pipe 102 at the maximum vibration displacement position 201 of the "C-type” mode shape can be less than a predetermined vibration displacement value, and when the exhaust pipe 102 When vibrating with the first or second "S-type” mode, the exhaust pipe 102 is at the maximum vibration displacement position 212, 213 of the first "S-type” mode or the maximum vibration displacement position 222 of the second "S-type” mode
  • the vibration displacements at , 223 can also be smaller than the predetermined vibration displacement value, so that the vibration of the exhaust pipe 102 will not damage the exhaust pipe 102 and the variable frequency screw unit 10 .
  • the predetermined vibration displacement value is 60 ⁇ m
  • the predetermined frequency difference is 10-15 Hz.
  • the counterweights 401 and 402 can be configured to have a weight of 3 kg respectively.
  • the present application arranges counterweights on the exhaust pipe 102, and controls the different counterweight positions of the counterweights on the exhaust pipe 102 according to the current vibration of the exhaust pipe 102, so that the exhaust pipe can be maintained or changed as required 102 mass distribution and stiffness. Therefore, the present application can maintain or change the natural vibration frequency of the exhaust pipe 102 according to the current vibration situation of the exhaust pipe 102 according to actual needs, so as to ensure the exhaust pulsation frequency of the variable frequency screw compressor 101 and the natural vibration frequency of the exhaust pipe 102 The difference of is large enough, so that the vibration of the exhaust pipe 102 is small enough, so as not to cause adverse effects on the operation of the exhaust pipe 102 and the variable frequency screw unit 10 .
  • the vibration frequency adjustment system of the present application can continuously and effectively function.
  • the counterweights 401 , 402 are annular structures 403 , 405 .
  • a rolling device 414 is provided inside the annular structures 403 , 405 , so that the counterweights 401 and 402 can roll on the surface of the exhaust pipe 102 .
  • the rolling device 414 can be a roller or a ball.
  • three evenly distributed rolling devices 414 are provided on the inner side of the annular structures 403 , 405 , so that the counterweight can roll more smoothly and continuously on the exhaust pipe 102 .
  • the annular structures 403, 405 may be eccentric rings.
  • the use of ring structures 403, 405 in the form of eccentric rings is conducive to maintaining the counterweights 401, 402 on the exhaust pipe 102 with a constant posture, thereby facilitating the relative position of the maintenance and driving devices 407, 408, and thus making the counterweights 401 , 402 can keep rolling smoothly and continuously on the exhaust pipe 102 .
  • the counterweight 401 can also include a guide rod 404 connected to the ring structure 403 for combining with the driving device 407.
  • the counterweight 402 can also include a guide rod 404 connected to the ring structure 405.
  • the guide rod 406 is used to combine with the driving device 408 .
  • the driving means 407 and 408 are hydraulic or pneumatic actuators.
  • the driving device 407 includes a cylinder body 409 and a push rod 410
  • the driving device 408 includes a cylinder body 411 and a push rod 412 .
  • One end of the push rod 410 of the driving device 407 is telescopically fixed in the cylinder body 409 , and the other end is combined with the guide rod 404 of the counterweight 401 , so that the counterweight 401 can be driven.
  • One end of the push rod 412 of the driving device 408 is telescopically fixed in the cylinder body 411 , and the other end is combined with the guide rod 406 of the counterweight 402 , so that the counterweight 402 can be driven.
  • At least a portion of the exhaust duct 102 may be configured to slope along its length.
  • the driving devices 407, 408 In order to enable the driving devices 407, 408 to drive the counterweights 401, 402 to move on the exhaust pipe 102 inclined along the length direction, it is desirable that the push rods 410, 412 of the driving devices 407, 408 can move along the counterweights 401, 402
  • the height direction of the guide rods 404, 406 moves up and down.
  • Fig. 4C further shows an enlarged view of the structure of the push rod 410 of the driving device 407 and the guide rod 404 of the counterweight 401, which enables this movement. As shown in FIG.
  • the guide rod 404 of the counterweight 401 is provided with a guide rail groove 413, and the end of the push rod 410 of the driving device 407 that is not fixed in the cylinder 409 is engaged in the guide rail groove 413 of the guide rod 404, And the push rod 410 and the guide rod 404 are substantially perpendicular, and the driving device 407 is configured to be able to rotate within the plane defined by the push rod 410 and the guide rod 404 .
  • the structural arrangement of the counterweight 401 and the driving device 407 makes it possible that when the counterweight 401 moves obliquely downward along the exhaust pipe 102 , the push rod 410 of the driving device 407 moves upward along the height of the guide rail groove 413 in the guide rail groove 413 .
  • the driving device 407 can keep driving the counterweight 401 .
  • FIG. 4C Only the connection between the guide rod 404 of the counterweight 401 and the push rod 410 of the driving device 407 is shown in FIG. 4C , it should be understood that the counterweight 402 and its driving device 408 can also be connected in a similar manner as required.
  • the push rods 410, 412 of the drive units 407, 408 need not be configured to follow the counterweights 401,
  • the guide rods 404 , 406 of 402 move in the height direction, so that the push rods 410 , 412 of the driving devices 407 , 408 and the guide rods 404 , 406 of the counterweights 401 , 402 can also be designed to have different configurations.
  • FIGS. 5A-5B are an alternative embodiment to the weight arrangement shown in Figures 4A-4B.
  • the embodiment of FIGS. 5A and 5B is similar to the embodiment of FIGS. 4A to 4B , the only difference is that only one counterweight 401 is used in the embodiment of 5A to 5B.
  • the controller 307 determines which vibration mode the exhaust pipe 102 is vibrating in, the controller 307 controls the driving device 407 so that the counterweight 401 remains at or moves to the “S-type” mode-type counterweight position 421 or the “C-type” vibration mode.
  • the counterweight 401 can be configured to have a weight of 6 kg, for example.
  • a traction mechanism formed by a combination of a motor, a traction rope and a fixed pulley can be used as a driving device to move the counterweight.
  • the counterweight may be connected to the traction rope so that the counterweight moves along with the circular movement of the traction rope during the circular movement of the traction rope driven by the motor.
  • the controller controls the motor to rotate in the first direction
  • the traction rope moves circularly in the first direction, so that the motor moves to a counterweight position along with the movement of the traction rope.
  • the controller controls the motor to rotate in the second direction
  • the traction rope moves circularly in the second direction, so that the motor moves to another counterweight position along with the movement of the traction rope.
  • a limiter can be set at the counterweight position, so that the controller can judge that the counterweight block has moved to the counterweight position, thereby controlling the motor to stop rotating.
  • the counterweight may be configured to include only the ring structure shown in Figures 4A-5B, without including guide rods connected to the ring structure.
  • FIG. 6 shows a schematic block diagram of the controller 307 .
  • the controller 307 includes a bus 601 .
  • a processor 602 a memory 603 , a mass storage device 604 , an input interface 605 and an output interface 606 are connected to the bus 601 .
  • the input interface and output interface may be wireless control modules.
  • the processor 602 can read out the program (or instruction) from the memory 603 or the mass storage device 604, and execute the program (or instruction) to perform the control function to the drive devices 407, 408; the processor 602 can also transfer data or The instructions are written into memory 603 or mass storage device 604 .
  • the memory 603 and the mass storage device 604 can store programs (instructions) or data.
  • the memory 603 has a faster access speed than that of the mass storage device 604 , and the mass storage device 604 has a memory size larger than that of the memory 603 .
  • the processor 602 can control the memory 603 , the mass storage device 604 , the input interface 605 and the output interface 606 .
  • the input interface 605 receives input from the variable frequency screw compressor 101 or the sensors 301 , 302 , 303 , 304 , 305 and 306 and converts the received input into a signal recognizable by the processor 602 .
  • the output interface 606 receives control signals from the processor 602 and converts the control signals into outputs suitable for the drive means 407 , 408 .
  • the processor 602 performs desired functions according to the received input. Also in operation, when a control signal is received from the processor 602, the output interface 606 converts the control signal into an output, and uses the converted output to the drive means 407, 408 to control the drive means 407, 408 to place the counterweight The blocks 401 , 402 remain in or move to the appropriate counterweight position on the exhaust duct 102 .
  • the counterweight is a certain distance from the maximum vibration displacement position of the exhaust pipe, so that the counterweight is not easy to be damaged, and it is not easy to separate from the exhaust pipe.

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Abstract

一种振动频率调节系统，包括可振动部件（102）、至少一个配重块（401，402）、至少一个驱动装置（407、408）和控制器（307），可振动部件（102）被构造为与振动源（101）连接，振动源（101）具有工作频率范围，可振动部件（102）具有固有振动频率，至少一个配重块（401，402）被构造为可沿所述可振动部件（102）移动，至少一个驱动装置（407、408）被构造为能够使得至少一个配重块（401、402）保持在或移动至可振动部件（102）上的不同的配重位置（421、422、423），控制器（307）通信连接所述至少一个驱动装置（407、408）。该振动频率调节系统用于变频螺杆机组，以减小排气管道的振动。

Description

振动频率调节系统 技术领域
本申请涉及振动频率调节系统，尤其是用于变频螺杆机组的振动频率调节系统。
背景技术
变频螺杆机组中的变频螺杆压缩机以一定的频率向排气管道排出气体。当变频螺杆压缩机的工作频率和排气管道的固有振动频率相同或相近时，容易产生共振。希望能够对排气管道进行避振调节，以减小共振带来的影响。
发明内容
本申请提供一种振动频率调节系统，该调节系统能够对排气管道的固有振动频率进行调节调节，使得减小排气管道的振动。
根据本申请的一个方面，本申请的振动频率调节系统包括，可振动部件、至少一个配重块、至少一个驱动装置和控制器。所述可振动部件被构造为与振动源连接，所述振动源具有工作频率范围，所述可振动部件具有固有振动频率。所述至少一个配重块被构造为可沿所述可振动部件移动。所述至少一个驱动装置被构造为能够使得所述至少一个配重块保持在或移动至所述可振动部件上的不同的配重位置。所述控制器通信连接所述至少一个驱动装置。
如上所述的振动频率调节系统，当所述可振动部件振动时，所述可振动部件上具有至少一个最大振动位移位置。所述控制器被配置为，当所述可振动部件振动时，所述控制器能够控制所述至少一个驱动装置，使得所述至少一个配重块被保持在偏离或移动至偏离所述可振动部件上的所述至少一个最大振动位移位置。
如上所述的振动频率调节系统，所述的控制器被配置为，能够通过控制所述至少一个驱动装置驱动所述至少一个配重块在所述配重位置中的对应的两个预设的配重位置间切换。
如上所述的振动频率调节系统，所述控制器被配置为，能够通过控制所述至少一个驱动装置中的每一个驱动装置分别驱动所述至少一个配重块中的每一个配重块在所述配重位置中的对应的两个预设的配重位置间切换。
如上所述的振动频率调节系统，所述可振动部件在所述振动源的所述工作频率范围内能够以“C型”振型或“S型”振型发生振动。所述的配重位置包括“C型”振型配重位置和“S型”振型配重位置。所述控制器被配置为能够根据所述可振动部件的振型来控制所述至少一个驱动装置：当所述可振动部件以所述“C型”振型振动时，所述控制器控制所述至少一个驱动装置使得所述至少一个配重块被保持在或移动至所述“C型”振型配重位置；或者，当所述可振动部件以所述“S型”振型振动时，所述控制器控制所述至少一个驱动装置使得所述至少一个配重块被保持在或移动至所述“S型”振型配重位置。
如上所述的振动频率调节系统，当所述可振动部件以所述“C型”振型振动时，所述可振动部件具有一个“C型”振型最大振动位移位置，所述“C型”振型配重位置与所述的“C型”振型最大振动位移位置相隔一定距离。当所述可振动部件以所述“S型”振型振动时，所述可振动部件具有一个“S型”振型最小振动位移位置和两个“S型”振型最大振动位移位置，所述两个“S型”振型最大振动位移位置分别为“S型”振型第一最大振动位移位置和“S型”振型第二最大振动位移位置，所述“S型”振型配重位置与所述两个“S型”振型最大振动位移位置相隔一定距离。
如上所述的振动频率调节系统，所述“C型”振型配重位置包括“C型”振型第一配重位置和“C型”振型第二配重位置。所述“C型”振型第一配重位置位于所述“C型”振型最大振动位移位置的一侧，所述“C型”振型第二配重位置位于所述“C型”振型最大振动位移位置的另一侧。所述“S型”振型配重位置位于所述“S型”振型最小振动位移位置处。
如上所述的振动频率调节系统，所述“C型”振型第一配重位置邻近所述“S型”振型第一最大振动位移位置，所述“C型”振型第二配重位置邻近所述“S型”振型第二最大振动位移位置。
如上所述的振动频率调节系统，所述至少一个配重块被构造为具有预定的重量，所述至少一个配重块的所述预定重量使得：当所述可振动部件以所述“C型”振型振动时，所述可振动部件在所述“C型”振型最大振动位移位置处的振动位移小于预定振动位移值；和当所述可振动部件以所述“S型”振型振动时，所述可振动部件在所述两个“S型”振型最大振动位移位置处的振动位移都小于所述预定振动位移值。
如上所述的振动频率调节系统，所述至少一个驱动装置的数量是两个，分别是第一驱动装置和第二驱动装置。所述至少一个配重块的数量是两个，分别是第一配重块和第二配重块。当所述可振动部件以所述“C型”振型振动时，所述第一配重块被保持在或移动至所述“C型”振型第一配重位置，且所述第二配重块被保持在或移动至所述“C型”振型第二配重位置，或当所述可振动部件以所述“S型”振型振动时，所述第一配重块和所述第二配重块都被保持在或移动至所述“S型”振型配重位置。
如上所述的振动频率调节系统，所述控制器被配置为：存储所述可振动部件的固有振动频率，所述的固有振动频率至少包括“C型”振型固有振动频率和“S型”振型固有振动频率；获取可振动部件的当前振动频率；和比较所述可振动部件的所述当前振动频率和所述可振动部件的所述固有振动频率。当所述控制器判断所述可振动部件的所述当前振动频率与所述可振动部件的所述“C型”振型固有振动频率之间的偏差小于一预设阈值时，所述控制器判断所述可振动部件以“C型”振型振动，或当所述控制器判断所述可振动部件的所述当前振动频率与所述可振动部件的所述“S型”振型固有振动频率之间的偏差小于一预设阈值时，所述控制器判断所述可振动部件以“S型”振型振动。获取所述可振动部件的所述当前振动频率的方法包括：(1)所述控制器从所述的振动源接收指示所述振动源的所述工作频率的信号，并将所述的振动源的所述工作频率作为所述可振动部件的所述当前振动频率；或(2)将所述振动频率调节系统构造为包括频率探测装置，用于探测所述可振动部件的所述当前振动频率，所述控制器从所述频率探测装置接收指示所述可振动部件的所述当前振动频率的信号。
如上所述的振动频率调节系统，所述振动频率调节系统还包括探测装置，用于探测所述可振动部件的振动情况，所述探测装置通信连接所述控制器。所述探测装置包括：第一位置探测装置、第二位置探测装置和第三位置探测装置。所述第一位置探测装置设置在所述可振动部件的第一探测位置处以探测所述可振动部件在所述第一探测位置处的振动情况，所述第一探测位置位于所述“C型”振型最大振动位移位置处。所述第二位置探测装置设置在所述可振动部件的第二探测位置处以探测所述可振动部件在所述第二探测位置处的振动情况，所述第二探测位置位于所述“S型”振型第一最大振动位移位置处。所述第三位置探测装置设置在所述可振动部件的第三探测位置处以探测所述可振动部件在所述第三探测位置处的振动情况，所述第三探测位置位于所述“S型”振型第二最大振动位移位置处。
如上所述的振动频率调节系统，所述第一位置探测装置包括第一方向第一传感器和第二方向第一传感器，所述第二位置探测装置包括第一方向第二传感器和第二方向第二传感器， 所述第三位置探测装置包括第一方向第三传感器和第二方向第三传感器。所述控制器被配置为：基于所述第一位置探测装置中的所述第一方向第一传感器的检测，确定所述可振动部件在所述第一探测位置处在第一方向上的振动位移Y1；基于所述第一位置探测装置中的所述第二方向第一传感器的检测，确定所述可振动部件在所述第一探测位置处在第二方向上的振动位移Z1；基于所述第二位置探测装置中的所述第一方向第二传感器的检测，确定所述可振动部件在所述第二探测位置处在所述第一方向上的振动位移Y2；基于所述第二位置探测装置中的所述第二方向第二传感器的检测，确定所述可振动部件在所述第二探测位置处在所述第二方向上的振动位移Z2；基于所述第三位置探测装置中的所述第一方向第三传感器的检测，确定所述可振动部件在所述第三探测位置处在所述第一方向上的振动位移Y3；和基于所述第三位置探测装置中的所述第二方向第三传感器的检测，确定所述可振动部件在所述第三探测位置处在所述第二方向上的振动位移Z3。
如上所述的振动频率调节系统，当所述控制器判断Z2<Y2、Z1<Y1、Z3<Y3，且Y2和Y3都小于预定振动位移值、Y1大于预定振动位移值时，所述控制器判断所述可振动部件以所述“C型”振型发生振动。或者，当所述控制器判断：(i)Y2<Z2、Y1<Z1、Y3<Z3、Z1<Z2、Z1<Z3，且Z2和Z3都大于所述预定振动位移值，或(ii)Y2>Z2、Y1>Z1、Y3>Z3、Y1<Y2、Y1<Y3，且Y2和Y3都大于所述预定振动位移值，所述控制器判断所述可振动部件以所述“S型”振型发生振动。
如上所述的振动频率调节系统，所述探测装置是单向位移传感器或单向加速度传感器。
如上所述的振动频率调节系统，所述至少一个配重块为环状结构，所述的环状结构的内侧设置有滚动装置，所述的滚动装置是滚轮或滚珠，所述的滚动装置能够在所述的可振动部件的表面滚动。
如上所述的振动频率调节系统，其特征在于：所述环状结构为偏心环。
如上所述的振动频率调节系统，其特征在于：所述的环状结构的内侧设置有三个均匀分布的滚动装置。
如上所述的振动频率调节系统，所述至少一个驱动装置是气动或液压执行元件，所述至少一个驱动装置包括缸体和推杆，所述推杆的一端可伸缩地固定在在所述缸体内，所述推杆的另一端连接所述至少一个配重块中对应的一个配重块。
如上所述的振动频率调节系统，所述振动源是变频螺杆压缩机，所述可振动部件是与所述变频螺杆压缩机的排气口相连的排气管道。
附图说明
图1是根据现有技术的变频螺杆机组的一个实施例的结构立体示意图。
图2A-2C示出根据本申请测试得到的对应于排气管道的不同固有振动频率的振型。
图3示出根据本申请确定排气管道正在以何种阵型发生振动的一个实施方式的结构示意图。
图4A至4C是根据本申请的配重块设置的一个实施方式的结构示意图。
图5A至5B是根据本申请的配重块设置的另一个实施方式的结构示意图。
图6是根据本申请的控制器的框图。
具体实施方式
下面将参考构成本说明书一部分的附图对本申请的各种具体实施方式进行描述。应该理解的是，在可能的情况下，本申请中使用的相同或者相类似的附图标记指的是相同的部件。
图1是根据现有技术的变频螺杆机组10的结构立体示意图。如图1所示，变频螺杆机组10包括变频螺杆压缩机101、排气管道102、蒸发器103和冷凝器104。变频螺杆压缩机101的进气口连接蒸发器103的出气口。排气管道102的进气口和变频螺杆压缩机101的排气口连接，排气管道102的出气口和冷凝器104连接。从而，变频螺杆压缩机101能够将来自蒸发器103中的气态冷媒压缩后经排气管道102输送至冷凝器104。变频螺杆压缩机101以一定范围内的排气脉动频率将经压缩的气态冷媒输送到排气管道102。当变频螺杆压缩机101的排气脉动频率达到或接近排气管道102的固有振动频率时，排气管道102产生共振。当排气管道102发生共振，排气管道102的振幅和应力应变很大，这会降低排气管道102的使用寿命。并且，由于排气管道102的振动会带动变频螺杆压缩机101、蒸发器103、冷凝器104及设置在这些器件上的零件的振动，排气管道102的过大振动也会影响变频螺杆机组10的正常运行。另外，排气管道102发生共振时产生的过大振动还会带来噪声问题。
如下文中具体讨论的，本申请在排气管道102上的选定配重位置处设置配重块。为了避免配重块在排气管道102发生振动时被损害或者与排气管道102脱离，本申请选定的配重位置和排气管道102的最大振动位移位置相距一定距离。并且，本申请根据排气管道102的当前振动情况控制配重块位于排气管道102上的不同配重位置，使得能够根据需要保持或改变排气管道102的质量分布和刚度。从而，本申请可以根据排气管道102的当前振动情况，按照实际需要保持或改变排气管道102的固有振动频率，确保变频螺杆压缩机101的排气脉动频率和排气管道102的固有振动频率的差值足够大，使得排气管道102的振动足够小，不致于对排气管道102和变频螺杆机组10的运行造成不利影响。如下文中所讨论的，本申请可以在变频螺杆压缩机101向排气管道102排气时，确定排气管道102正在以何种振型发生振动，并基于此使得配重块保持在或移动至排气管道102上的相应配重位置。
可以通过多种方式来确定排气管道102正在以何种振型发生振动。结合图2A至图3具体讨论确定排气管道102正在以何种振型发生振动的一种示例实施方式，在该实施方式中，预先对排气管道102进行测试得到该类型排气管道102的固有振动频率下的对应振型。之后在变频螺杆机组10的工作过程中，在变频螺杆压缩机101向排气管道102排气的时候，实时探测排气管道102发生振动的时候在多个位置处的振动位移情况来判断排气管道102正在以何种振型发生振动。
可以使用仿真分析方法(如，根据中国的国家标准GB/T33582-2017《机械产品结构有限元力学分析通用规则》)预先测试得到排气管道102在固有振动频率下的对应振型。在变频螺杆压缩机101的一个实施例中，变频螺杆压缩机101的排气脉动频率在80～250Hz的范围之间。本申请的发明人通过测试发现排气管道102在80～250Hz的频率范围之间具有三个固有振动频率，在排气管道102的实际振动频率达到或接近这三个固有振动频率时，排气管道102分别以对应的三种振型发生振动。图2A-2C示意性示出排气管道102的这三种振型。
图2A示出排气管道102的“C型”振型。在图2A所示的“C型”振型中，排气管道102在Y轴方向(排气管道102的高度方向)上发生“C型”振动，并在位置201处具有“C型”振型最大振动位移。
图2B示出排气管道102的第一“S型”振型。在图2B所示的第一“S型”振型中，排气管道102在Z轴方向(同时垂直于排气管道102的长度和高度的方向)上发生“S型”振动，并在位置212、213处具有第一“S型”振型最大振动位移，而在位置211处具有第一“S型”振型最小振动位移。
图2C示出排气管道102的第二“S型”振型。在图2C所示的第二“S型”振型中，排气管道102在Y轴方向(管道的高度方向)上发生“S型”振动，并在位置222和223处具有第二“S型”振型最大振动位移，而在位置221处具有第二“S型”振型最小振动位移。
排气管道102的“C型”振型最大振动位移位置201、第一“S型”振型最小振动位移位置211和第二“S型”振型最小振动位移位置221大致重合，排气管道102的第一“S型”振型最小振动位移位置211和第二“S型”振型最小振动位移位置221大致重合，排气管道102的第一“S型”振型最大振动位移位置212和第二“S型”振型最大振动位移位置222大致重合，第一“S型”振型最大振动位移位置213和第二“S型”振型最大振动位移位置223大致重合。对排气管道102的振型探测结果被存储在控制器(在图3中示出)中。
图3示出用于在变频螺杆压缩机101向排气管道102排气的过程中，实时确定排气管道102正在以何种阵型发生振动的一种实施方式的结构示意图。在该实施方式中，通过探测排气管道102在不同位置处的振动位移情况来确定排气管道102正在以何种阵型发生振动。如图3所示，在排气管道102上设置三个探测位置311、312、313。第一探测位置311设置在“C型”振型最大振动位移位置201处，第二探测位置312设置在第一“S型”振型最大振动位移位置212(也即，第二“S型”振型最大振动位移位置222)处，第三探测位置313设置在第一“S型”振型最大振动位移位置213(也即，第二“S型”振型最大振动位移位置223)处。第一位置探测装置包括第一方向第一传感器301和第二方向第一传感器302，第一方向第一传感器301用于检测排气管道102在第一探测位置311处在Y轴方向的振动情况，第二方向第一传感器302用于检测排气管道102在第一探测位置311处在Z轴方向的振动情况。在第二探测位置312处设置第二位置探测装置。第二位置探测装置包括第一方向第二传感器303和第二方向第二传感器304，第一方向第二传感器303用于检测排气管道102在第二探测位置312处在Y轴方向的振动情况，第二方向第二传感器304用于检测排气管道102在第二探测位置312处在Z轴方向的振动情况。在第三探测位置313处设置第三位置探测装置。第三位置探测装置包括第一方向第三传感器305和第二方向第三传感器306，第一方向第三传感器305用于检测排气管道102在第三探测位置313处在Y轴方向的振动情况，第二方向第三传感器306用于检测排气管道102在第三探测位置313处在Z轴方向的振动情况。
如图3所示，变频螺杆机组10还包括一控制器307，该控制器307通信连接传感器301、302、303、304、305、306，以从传感器301、302、303、304、305、306接收指示排气管道102在相应探测位置处的振动情况的信号。控制器307根据接收到的指示排气管道102在三 个探测位置311、312、313处的振动情况的信号，确定排气管道102在这些位置处的振动位移，进而确定排气管道102正在以何种振型发生振动。具体来说，控制器307基于从第一方向第一传感器301接收到的信号，确定排气管道102在第一探测位置311处在Y轴方向上的振动位移Y1,基于从第二方向第一传感器302接收到的信号，确定排气管道102在第一探测位置311处在Z轴方向上的振动位移Z1,基于从第一方向第二传感器303接收到的信号，确定排气管道102在第二探测位置312处在Y轴方向上的振动位移Y2,基于从第二方向第二传感器304接收到的信号，确定排气管道102在第二探测位置312处在Z轴方向上的振动位移Z2,基于从第一方向第三传感器305接收到的信号，确定排气管道102在第三探测位置313处在Y轴方向上的振动位移Y3，基于从第二方向第三传感器306接收到的信号，确定排气管道102在第三探测位置313处在Z轴方向上的振动位移Z3。控制器307随后比较排气管道102在三个探测位置311、312、313处的振动位移，以确定排气管道102正在以何种振型发生振动。当控制器307判断Z2<Y2、Z1<Y1、Z3<Y3，且Y2和Y3都小于预定振动位移值，且Y1大于所述预定振动位移值时，控制器307判断所述排气管道102正在以“C型”振型发生振动。当控制器307判断Y2<Z2、Y1<Z1、Y3<Z3、Z1<Z2、Z1<Z3，且Z2和Z3都大于预定振动位移值，控制器307判断排气管道102正在以第一“S型”振型发生振动。当控制器307判断Y2>Z2、Y1>Z1、Y3>Z3、Y1<Y2、Y1<Y3，且Y2和Y3都大于预定振动位移值，控制器307判断排气管道102正在以第二“S型”振型发生振动。预定振动位移值被设定成，当振动位移不超过该数值，将不会对排气管道102和变频螺杆机组10造成损害。在一个实施例中，该预定振动位移值被设定为60μm。
传感器301、302、303、304、305、306可以都是单向加速度传感器，用于检测排气管道102在各个探测位置处在Y轴和Z轴方向上的运动加速度，并向控制器307发送指示检测到的运动加速度的信号。控制器307能够基于来自这些单向加速度传感器的加速度信号计算得到排气管道102在各个探测位置处的振动位移。传感器301、302、303、304、305、306也可以都是单向位移传感器，用于检测排气管道102在各个探测位置处在Y轴和Z轴方向上的振动位移，并向控制器307发送指示检测到的振动位移的信号。
除了上述通过比较排气管道102在各振型的最大振动位移位置处的振动位移来确定排气管道102正在以何种振型发生振动的实施方式以外，在其他实施方式中，也可以通过确定排气管道102在发生振动时的当前振动频率，并比较排气管道102的当前振动频率和其固有振动频率来确定其当前振型。
在该实施方式中，可以预先使用试验模态方法对已经安装在特定变频螺杆机组10中的排气管道102进行测试来确定其固有振动频率及其对应振型。通过该测试方法可以发现，在变频螺杆压缩机101的排气脉动频率在80～250Hz的范围之间时，排气管道102同样具有三个固有振动频率及如图2A至2C所示的三种对应振型。测试结果存储在控制器307中。
之后，在变频螺杆机组10的工作过程中，控制器307实时确定排气管道102在发生振动时的当前振动频率。例如，控制器307可以从变频螺杆压缩机101接收指示变频螺杆压缩机101的排气脉动频率的信号，并将变频螺杆压缩机101的排气脉动频率作为排气管道102的当前振动频率。又例如，控制器307也可以从排气管道102的频率探测装置接收指示排气管道102的振动情况的信号，并基于该信号进行频谱分析来确定排气管道102的当前振动频率。在从排气管道102的频率探测装置接收指示排气管道102的振动情况的信号的示例中，该频率探测装置可以是如图3中设置的六个单向加速度传感器或单向位移传感器，也可以是在排气管道102的任意三个位置上设置的三个三向加速度传感器或三向位移传感器。
在控制器307通过确定排气管道102的当前振动频率来确定其当前振型的实施方式中，当排气管道102的当前振动频率和对应排气管道102的“C型”振型的“C型”固有振动频率的差值小于一预设值时，控制器307判断排气管道102正在以“C型”振型发生振动。当排气管道102的当前振动频率和对应排气管道102的第一“S型”振型的第一“S型”固有振动频率的差值小于一预设值时，控制器307判断排气管道102正在以第一“S型”振型发生振动。当排气管道102的当前振动频率和对应排气管道102的第二“S型”振型的第二“S型”固有振动频率的差值小于一预设值时，控制器307判断排气管道102正在以第二“S型”振型发生振动。排气管道102的当前振动频率和各固有振动频率的差值的预设值可以是4Hz。
在控制器307确定排气管道102正在以何种振型发生振动后，控制器307保持或调整配重块的位置来保持或改变排气管道102的固有振动频率，以确保排气管道102的固有振动频率和变频螺杆压缩机101的排气脉动频率之差足够大，从而使得排气管道102的振动足够小，不致于损害排气管道102和变频螺杆机组10。结合图4A至4C和图5A至5B示出的配重块设置的不同实施方式说明对配重块位置的保持或调整。
在图4A至4C所示的实施方式中，在排气管道102上设置两个配重块401和402。在排气管道102上还设置两个驱动装置407和408，驱动装置407和配重块401相连，用于驱动配重块401，驱动装置408和配重块402相连，用于驱动配重块402。如图4A和4B所示，驱动装置407和驱动装置408分别和控制器307通信连接，从而控制器307可以控制驱动装置 407和408驱动配重块401和402。同样如图4A和4B所示，排气管道102上设有三个配重位置421、422、423,控制器307可以控制驱动装置407使得配重块401移动至配重位置421或422，控制器307可以控制驱动装置408使得配重块402移动至配重位置421或423。第一配重位置421被设置为与排气管道102的第一“S型”振型最大振动位移位置212、213(也即，第二“S型”振型最大振动位移位置222、223)都相隔一定距离。第二配重位置422位于“C型”振型最大振动位移位置201的一侧，与“C型”振型最大振动位移位置201相隔一定距离。第三配重位置423位于“C型”振型最大振动位移位置201的另一侧，与“C型”振型最大振动位移位置201相隔一定距离。在一个实施例中，第一配重位置421位于或邻近第一“S型”振型最小振动位移位置211(也即，第二“S型”振型最小振动位移位置221)处，第二配重位置422位于或邻近第一“S型”振型最大振动位移位置212(也即，第二“S型”振型最大振动位移位置222)处，第三配重位置423位于或邻近第一“S型”振型最大振动位移位置213(也即，第二“S型”振型最大振动位移位置223)处。
当控制器307确定排气管道102正在以“C型”振型振动时，若配重块401和402此时正处于第一配重位置421，控制器307控制驱动装置407将配重块401从第一配重位置421移动至第二配重位置422，并控制驱动装置408将配重块402从第一配重位置421移动至第三配重位置423；若此时配重块401已经处于第二配重位置422，且配重块402已经处于第三配置位置423，控制器307控制驱动装置407将第一配重块401保持在第二配重位置422，并控制驱动装置408将第二配重块402保持在第三配重位置423。当控制器307确定排气管道102正在以第一“S型”或第二“S型”振型振动，若此时配重块401处于第二配重位置422，且配重块402处于第三配置位置423，控制器307控制驱动装置407将第一配重块401移动至第一配重位置421，并控制驱动装置408将第二配重块402也移动至第一配重位置421；若此时配重块401和402已经处于第一配重位置421，控制器307控制驱动装置407将第一配重块401保持在第一配重位置421，并控制驱动装置408将第二配重块402也保持在第一配重位置421。
配重块401、402被构造成具有预定重量。该预定重量使得，当排气管道102以“C型”振型振动时，在配重块401、402位于“C型”振型的相应配重位置422和423的情况下，排气管道102的固有振动频率和变频螺杆机组10的排气脉动频率之差达到一预定频率差，且当排气管道102以第一或第二“S型”振型振动时，在配重块401、402位于第一或第二“S型”振型的相应配重位置421时，排气管道102的固有振动频率和变频螺杆机组10的排气脉动频率之差也达到该预定频率差。从而，当排气管道102以“C型”振型振动时，排气管道102 在“C型”振型最大振动位移位置201处的振动位移能够小于预定振动位移值，且当排气管道102以第一或第二“S型”振型振动时，排气管道102在第一“S型”振型最大振动位移位置212、213处或第二“S型”振型最大振动位移位置222、223处的振动位移也都能够小于预定振动位移值，从而排气管道102的振动不致于损害排气管道102和变频螺杆机组10。在一个实施例中，预定振动位移值是60μm，预定频率差是到10～15Hz,为实现该预定频率差，配重块401、402可以被构造成分别具有3kg的重量。
本申请通过在排气管道102上设置配重块，并根据排气管道102的当前振动情况控制配重块位于排气管道102上的不同配重位置，使得能够根据需要保持或改变排气管道102的质量分布和刚度。从而，本申请可以根据排气管道102的当前振动情况，按照实际需要保持或改变排气管道102的固有振动频率，确保变频螺杆压缩机101的排气脉动频率和排气管道102的固有振动频率的差足够大，使得排气管道102的振动足够小，不致于对排气管道102和变频螺杆机组10的运行造成不利影响。并且，由于本申请将配重块设置在处于距离当前振型下的最大振动位移位置一定距离处，在排气管道102发生振动时，配重块不易被破坏，且不易与排气管道102脱离。因此，本申请的振动频率调节系统可以持续有效地起作用。
图4A至4C示出配重块401、402和驱动装置407、408的结构一个实施例。如图4A至4C所示，配重块401、402是环状结构403、405。环状结构403、405内侧设置有滚动装置414，使得配重块401和402可以在排气管道102的表面滚动。该滚动装置414可以是滚轮或滚珠。在配重块的一个实施例中，环状结构403、405的内侧设有三个均匀分布的滚动装置414，使得配重块在排气管道102上可以更为平滑、连续地滚动。作为一个示例，如图4C所示，环状结构403、405可以是偏心环。使用偏心环形式的环状结构403、405有利于配重块401、402以恒定的姿态保持在排气管道102上，从而有利于保持和驱动装置407、408的相对位置，进而使得配重块401、402能够在排气管道102上保持平滑、连续地滚动。如图4A至4C所示，配重块401还可以包括和环状结构403连接的导杆404，用于结合驱动装置407，类似地，配重块402还可以包括和环状结构405连接的导杆406，用于结合驱动装置408。
在图4A至4C所示的实施例中，驱动装置407和408是液压或气动执行元件。驱动装置407包括缸体409和推杆410，类似地，驱动装置408包括缸体411和推杆412。驱动装置407的推杆410的一端可伸缩地固定在缸体409内，另一端和配重块401的导杆404结合，从而能够驱动配重块401。驱动装置408的推杆412的一端可伸缩地固定在缸体411内，另一端和配重块402的导杆406结合，从而能够驱动配重块402。
如图4A和4B所示，排气管道102的至少一部分可以被构造成沿其长度方向倾斜。为了使驱动装置407、408能够驱动配重块401、402在沿长度方向倾斜的排气管道102上移动，希望驱动装置407、408的推杆410、412能够沿着配重块401、402的导杆404、406的高度方向上下移动。图4C进一步示出驱动装置407的推杆410和配重块401的导杆404的结构的放大图，所示结构使得能够实现这种移动。如图4C所示，配重块401的导杆404上设有导轨槽413，驱动装置407的推杆410的未固定在缸体409中的一端被接合在导杆404的导轨槽413中，且推杆410和导杆404大致垂直，并且驱动装置407被设置成能够在推杆410和导杆404限定的平面内旋转。配重块401和驱动装置407的这种结构设置使得，当配重块401沿排气管道102向下倾斜移动，驱动装置407的推杆410在导轨槽413内沿着导轨槽413的高度向上移动，而当配重块401沿排气管道102向上倾斜移动，驱动装置407的推杆410在导轨槽413内沿着导轨槽413的高度向下移动。从而，在配重块401沿排气管道102向下或向上倾斜移动时，驱动装置407能够保持对配重块401的驱动。尽管图4C中只示出配重块401的导杆404和驱动装置407的推杆410的连接，应当理解的是，配重块402和其驱动装置408也可以根据需要以类似方式连接。同样应该理解的是，如果排气管道102在其整个长度方向上是平直、不存在倾斜的，则驱动装置407、408的推杆410、412不需要被构造成沿着配重块401、402的导杆404、406的高度方向移动，从而驱动装置407、408的推杆410、412和配重块401、402的导杆404、406也可以被设计成具有不同的构造。
图5A至5B是4A至4B所示的配重块设置的替换实施例。图5A和5B的实施例和图4A至4B的实施方式类似，区别仅在于5A至5B的实施方式中仅使用一个配重块401。在控制器307判断出排气管道102正在以何种振型振动后，控制器307控制驱动装置407使得配重块401保持在或移动至“S型”振型配重位置421或“C型”振型第一配重位置422。在该只设置一个配重块的实施例中，配重块401例如可以被构成具有6kg的重量。
尽管本申请只示出了如图4A至5B所示的配重块401、402和驱动装置407、408的结构，应当理解的是，任何其他能够实现驱动装置对配重块的移动的结构都适用于本申请，且在本申请的精神之内。作为一个示例，可以使用电机、牵引绳和定滑轮组合形成的牵引机构作为驱动装置实现对配重块的移动。通过使得牵引绳经过定滑轮，牵引绳可以在电机的驱动下做环形运动。可以将配重块连接至牵引绳，从而在电机驱动牵引绳作环形运动的过程中，配重块随着牵引绳的环形运动而移动。在控制器控制电机以第一方向旋转时，牵引绳以第一方向作环形运动，从而电机随着牵引绳的运动移动至一个配重位置。在控制器控制电机以第二方向旋转时，牵引绳以第二方向作环形运动，从而电机随着牵引绳的运动移动至另一个配重位 置。可以在配重位置设置限位器，使得控制器能够判断配重块已经移动到配重位置，从而控制电机停止转动。在使用这种驱动装置的实施例中，配重块可以被构造成仅包括图4A至5B所示的环状结构，而不需要包括和环状结构连接的导杆。
图6示出控制器307的示意性框图。如图6所示，控制器307包括总线601。处理器602、存储器603、大容量存储装置604、输入接口605和输出接口606连接到总线601。输入接口和输出接口可以是无线控制模块。处理器602可以从存储器603或大容量存储装置604中读出程序(或指令)，并执行该程序(或指令)以执行对驱动装置407、408的控制功能；处理器602还可以将数据或指令写入存储器603或大容量存储装置604中。存储器603和大容量存储装置604可以存储程序(指令)或数据。通常，存储器603具有比大容量存储装置604的访问速度快的访问速度，而大容量存储装置604具有比存储器603的存储器尺寸大的存储器尺寸。通过执行存储器603中的指令，处理器602可以控制存储器603、大容量存储装置604、输入接口605和输出接口606。输入接口605从变频螺杆压缩机101或传感器301、302、303、304、305和306接收输入，并将接收的输入转换成处理器602可识别的信号。输出接口606从处理器602接收控制信号，并将控制信号转换为适合驱动装置407、408的输出。
在操作中，当通过输入接口605从变频螺杆压缩机101或传感器301、302、303、304、305和306接收到输入，处理器602根据接收到的输入来执行所需功能。同样在操作中，当从处理器602接收到控制信号时，输出接口606将控制信号转换成输出，并将转换后的输出使用到驱动装置407、408，以控制驱动装置407、408将配重块401、402保持在或移动至排气管道102上合适的配重位置。
本申请至少包括以下技术效果：
1.减小排气管道的振动，从而减少变频螺杆机组使用过程中的噪声；
2.减小排气管道的振动，从而延长排气管道的使用寿命，确保变频螺杆机组的正常运行；
3.配重块距离排气管道最大振动位移位置一定距离，使得配重块不易被破坏，且不易与排气管道脱离。

Claims (20)

  1. 一种振动频率调节系统，其特征在于：所述振动频率调节系统包括：
    可振动部件(102)，所述可振动部件(102)被构造为与振动源(101)连接，所述振动源(101)具有工作频率范围，所述可振动部件(102)具有固有振动频率；
    至少一个配重块(401，402)，所述至少一个配重块被构造为可沿所述可振动部件(102)移动；
    至少一个驱动装置(407、408)，所述至少一个驱动装置被构造为能够使得所述至少一个配重块(401、402)保持在或移动至所述可振动部件(102)上的不同的配重位置(421、422、423)；
    控制器(307)，所述控制器(307)通信连接所述至少一个驱动装置(407、408)。
  2. 根据权利要求1所述的振动频率调节系统，其特征在于：
    当所述可振动部件(102)振动时，所述可振动部件(102)上具有至少一个最大振动位移位置；
    所述控制器(307)被配置为，当所述可振动部件(102)振动时，所述控制器(307)能够控制所述至少一个驱动装置(407、408)，使得所述至少一个配重块(401，402)被保持在偏离或移动至偏离所述可振动部件(102)上的所述至少一个最大振动位移位置。
  3. 根据权利要求2所述的振动频率调节系统，其特征在于：
    所述的控制器(307)被配置为，能够通过控制所述至少一个驱动装置(407、408)驱动所述至少一个配重块(401、402)在所述配重位置(421、422、423)中的对应的两个预设的配重位置(421、422、423)间切换。
  4. 根据权利要求3所述的振动频率调节系统，其特征在于：
    所述控制器(307)被配置为，能够通过控制所述至少一个驱动装置(407、408)中的每一个驱动装置(407、408)分别驱动所述至少一个配重块(401、402)中的每一个配重块(401、402)在所述配重位置(421、422、423)中的对应的两个预设的配重位置(421、422、423)间切换。
  5. 根据权利要求3所述的振动频率调节系统，其特征在于：
    所述可振动部件(102)在所述振动源(101)的所述工作频率范围内能够以“C型”振型或“S型”振型发生振动；
    所述的配重位置(421、422、423)包括“C型”振型配重位置(422，423)和“S型”振型配重位置(421)；和
    所述控制器(307)被配置为能够根据所述可振动部件(102)的振型来控制所述至少一个驱动装置：
    当所述可振动部件(102)以所述“C型”振型振动时，所述控制器(307)控制所述至少一个驱动装置(407、408)使得所述至少一个配重块(401，402)被保持在或移动至所述“C型”振型配重位置(422，423)；或
    当所述可振动部件(102)以所述“S型”振型振动时，所述控制器(307)控制所述至少一个驱动装置(407、408)使得所述至少一个配重块(401，402)被保持在或移动至所述“S型”振型配重位置(421)。
  6. 根据权利要求5所述的振动频率调节系统，其特征在于：
    当所述可振动部件(102)以所述“C型”振型振动时，所述可振动部件(102)具有一个“C型”振型最大振动位移位置(201)，所述“C型”振型配重位置(422，423)与所述的“C型”振型最大振动位移位置(201)相隔一定距离；
    当所述可振动部件(102)以所述“S型”振型振动时，所述可振动部件(102)具有一个“S型”振型最小振动位移位置(211，221)和两个“S型”振型最大振动位移位置(212、213，222，223)，所述两个“S型”振型最大振动位移位置(212、213，222，223)分别为“S型”振型第一最大振动位移位置(212，222)和“S型”振型第二最大振动位移位置(213，223)，所述“S型”振型配重位置(421)与所述两个“S型”振型最大振动位移位置(212、213，222，223)相隔一定距离。
  7. 根据权利要求6所述的振动频率调节系统，其特征在于：
    所述“C型”振型配重位置(422，423)包括“C型”振型第一配重位置(422)和“C型”振型第二配重位置(423)；
    所述“C型”振型第一配重位置(422)位于所述“C型”振型最大振动位移位置(201)的一侧，
    所述“C型”振型第二配重位置(423)位于所述“C型”振型最大振动位移位置(201)的另一侧；
    所述“S型”振型配重位置(421)位于所述“S型”振型最小振动位移位置(211，221)处。
  8. 根据权利要求7所述的振动频率调节系统，其特征在于：
    所述“C型”振型第一配重位置(422)邻近所述“S型”振型第一最大振动位移位置(212，222)；
    所述“C型”振型第二配重位置(423)邻近所述“S型”振型第二最大振动位移位置(213，223)。
  9. 根据权利要求7所述的振动频率调节系统，其特征在于
    所述至少一个配重块(401，402)被构造为具有预定的重量，所述至少一个配重块(401，402)的所述预定重量使得：
    当所述可振动部件(102)以所述“C型”振型振动时，所述可振动部件(102)在所述“C型”振型最大振动位移位置(201)处的振动位移小于预定振动位移值；和
    当所述可振动部件(102)以所述“S型”振型振动时，所述可振动部件(102)在所述两个“S型”振型最大振动位移位置(212、213，222，223)处的振动位移都小于所述预定振动位移值。
  10. 根据权利要求7所述的振动频率调节系统，其特征在于：
    所述至少一个驱动装置(407、408)的数量是两个，分别是第一驱动装置(407)和第二驱动装置(408)；
    所述至少一个配重块(401，402)的数量是两个，分别是第一配重块(401)和第二配重块(402)；
    当所述可振动部件(102)以所述“C型”振型振动时，所述第一配重块(401)被保持在或移动至所述“C型”振型第一配重位置(422)，且所述第二配重块(402)被保持在或移动至所述“C型”振型第二配重位置(423)；或
    当所述可振动部件(102)以所述“S型”振型振动时，所述第一配重块(401)和所述第二配重块(402)都被保持在或移动至所述“S型”振型配重位置(421)。
  11. 根据权利要求5所述的振动频率调节系统，其特征在于，
    所述控制器(307)被配置为：
    存储所述可振动部件(102)的固有振动频率，所述的固有振动频率至少包括“C型”振型固有振动频率和“S型”振型固有振动频率；
    获取可振动部件(102)的当前振动频率；和
    比较所述可振动部件(102)的所述当前振动频率和所述可振动部件(102)的所述固有振动频率；
    其中：
    当所述控制器(307)判断所述可振动部件(102)的所述当前振动频率与所述可振动部件(102)的所述“C型”振型固有振动频率之间的偏差小于一预设阈值时，所述控制器(307)判断所述可振动部件(102)以“C型”振型振动；或
    当所述控制器(307)判断所述可振动部件(102)的所述当前振动频率与所述可振动部件(102)的所述“S型”振型固有振动频率之间的偏差小于一预设阈值时，所述控制器(307)判断所述可振动部件(102)以“S型”振型振动；
    其中，获取所述可振动部件(102)的所述当前振动频率的方法包括：
    (1)所述控制器(307)从所述的振动源(101)接收指示所述振动源(101)的所述工作频率的信号，并将所述的振动源(101)的所述工作频率作为所述可振动部件(102)的所述当前振动频率；或
    (2)将所述振动频率调节系统构造为包括频率探测装置，用于探测所述可振动部件(101)的所述当前振动频率，所述控制器(307)从所述频率探测装置接收指示所述可振动部件(101)的所述当前振动频率的信号。
  12. 根据权利要求6所述的振动频率调节系统，其特征在于：
    所述振动频率调节系统还包括探测装置(301，302，333，304，305，306)，用于探测所述可振动部件(102)的振动情况，所述探测装置(301、302、303、304、305、306)通信连接所述控制器(307)，所述探测装置(301、302、303、304、305、306)包括：
    第一位置探测装置(301、302)，所述第一位置探测装置(301、302)设置在所述可振动部件(102)的第一探测位置(311)处以探测所述可振动部件(102)在所述第一探测位置(311)处的振动情况，所述第一探测位置(311)位于所述“C型”振型最大振动位移位置(201)处；
    第二位置探测装置(303、304)，所述第二位置探测装置(303、304)设置在所述可振动部件(102)的第二探测位置(312)处以探测所述可振动部件(102)在所述第二探测位置(312)处的振动情况，所述第二探测位置(312)位于所述“S型”振型第一最大振动位移位置(212，222)处；和
    第三位置探测装置(305、306)，所述第三位置探测装置(305、306)、设置在所述可振动部件(102)的第三探测位置(313)处以探测所述可振动部件(102)在所述第三探测位置(313)处的振动情况，所述第三探测位置(313)位于所述“S型”振型第二最大振动位移位置(213，223)处。
  13. 根据权利要求12所述的振动频率调节系统，其特征在于：
    所述第一位置探测装置(301、302)包括第一方向第一传感器(301)和第二方向第一传感器(302)；
    所述第二位置探测装置(303、304)包括第一方向第二传感器(303)和第二方向第二传感器(304)；
    所述第三位置探测装置(305、306)包括第一方向第三传感器(305)和第二方向第三传感器(306)；和
    所述控制器(307)被配置为基于：
    所述第一位置探测装置(301、302)中的所述第一方向第一传感器(301)的检测确定所述可振动部件(102)在所述第一探测位置(311)处在第一方向上的振动位移Y1,；
    所述第一位置探测装置(301、302)中的所述第二方向第一传感器(302)的检测确定所述可振动部件(102)在所述第一探测位置(311)处在第二方向上的振动位移Z1；
    所述第二位置探测装置(303、304)中的所述第一方向第二传感器(303)的检测确定所述可振动部件(102)在所述第二探测位置(312)处在所述第一方向上的振动位移Y2；
    所述第二位置探测装置(303、304)中的所述第二方向第二传感器(304)的检测确定所述可振动部件(102)在所述第二探测位置(312)处在所述第二方向上的振动位移Z2；
    所述第三位置探测装置(305、306)中的所述第一方向第三传感器(305)的检测确定所述可振动部件(102)在所述第三探测位置(313)处在所述第一方向上的振动位移Y3；和
    所述第三位置探测装置(305、306)中的所述第二方向第三传感器(306)的检测确定所述可振动部件(102)在所述第三探测位置(313)处在所述第二方向上的振动位移Z3。
  14. 根据权利要求13所述的振动频率调节系统，其特征在于：
    (1)当所述控制器(307)判断Z2<Y2、Z1<Y1、Z3<Y3，且Y2和Y3都小于预定振动位移值、Y1大于预定振动位移值时，所述控制器(307)判断所述可振动部件(102)以所述“C型”振型发生振动；或
    (2)当所述控制器(307)判断：
    (i)Y2<Z2、Y1<Z1、Y3<Z3、Z1<Z2、Z1<Z3，且Z2和Z3都大于所述预定振动位移值，或
    (ii)Y2>Z2、Y1>Z1、Y3>Z3、Y1<Y2、Y1<Y3，且Y2和Y3都大于所述预定振动位移值，
    所述控制器(307)判断所述可振动部件(102)以所述“S型”振型发生振动。
  15. 根据权利要求12所述的振动频率调节系统，其特征在于：所述探测装置(301、302、303、304、305、306)是单向位移传感器或单向加速度传感器。
  16. 根据权利要求1所述的振动频率调节系统，其特征在于：所述至少一个配重块(401、402)为环状结构(403、405)，所述的环状结构的内侧设置有滚动装置(414)，所述的滚 动装置(414)是滚轮或滚珠，所述的滚动装置能够在所述的可振动部件(102)的表面滚动。
  17. 根据权利要求16所述的振动频率调节系统，其特征在于：所述环状结构(403、405)为偏心环。
  18. 根据权利要求16所述的振动频率调节系统，其特征在于：所述的环状结构的内侧设置有三个均匀分布的滚动装置(414)。
  19. 根据权利要求4所述的振动频率调节系统，其特征在于：所述至少一个驱动装置(407、408)是气动或液压执行元件，所述至少一个驱动装置(407)包括缸体(409、411)和推杆(410、412)，所述推杆(410、412)的一端可伸缩地固定在在所述缸体(409、411)内，所述推杆(410、412)的另一端连接所述至少一个配重块(401、402)中对应的一个配重块(401、402)。
  20. 根据权利要求1所述的振动频率调节系统，其特征在于：所述振动源(101)是变频螺杆压缩机，所述可振动部件(102)是与所述变频螺杆压缩机的排气口相连的排气管道。
PCT/CN2022/117739 2021-09-26 2022-09-08 振动频率调节系统 Ceased WO2023045767A1 (zh)

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