CN1811189A - Screw compressor acoustic resonance reduction - Google Patents
Screw compressor acoustic resonance reduction Download PDFInfo
- Publication number
- CN1811189A CN1811189A CNA2006100060686A CN200610006068A CN1811189A CN 1811189 A CN1811189 A CN 1811189A CN A2006100060686 A CNA2006100060686 A CN A2006100060686A CN 200610006068 A CN200610006068 A CN 200610006068A CN 1811189 A CN1811189 A CN 1811189A
- Authority
- CN
- China
- Prior art keywords
- piston
- compressor
- barrier
- rotor
- valve component
- 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.)
- Pending
Links
Images
Classifications
-
- 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
- F04C29/068—Silencing the silencing means being arranged inside the pump housing
-
- 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
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/023—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where both members are moving
-
- 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
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/06—Silencing
- F04C29/061—Silencers using overlapping frequencies, e.g. Helmholtz resonators
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
A screw compressor for acoustic resonance reduction and refrigeration systems including the screw compressor are disclosed. The screw compressor has an acoustic barrier integral with the compressor housing for use with a slide valve assembly that includes a piston connected to a slide valve. A shaft connecting the slide valve and the piston passes through an aperture in the barrier with the piston and the slide valve disposed on opposite sides of the barrier. The acoustic barrier protects the piston from discharge pulses of compressed fluid exiting the rotors of the screw compressor, thus attenuating acoustic resonance, reducing compressor noise and premature wear of the slide valve assembly and compressor housing.
Description
Technical field
The present invention relates to a kind of screw compressor with the sliding shutter in the gas compression of being used in, more specifically, relate to a kind of reduce acoustic resonance, sliding shutter and compressor case wearing and tearing and compressor noise level be used to heat, the screw compressor of ventilation, air-conditioning and refrigeration system.
Background technique
Screw compressor is widely used in the gas of the many types of compression, and particularly those are used in heating, ventilation, air-conditioning and refrigeration (HVAC﹠amp; R) gas in the system.The capacity of screw compressor is typically controlled by the mechanism that is called sliding shutter.
The rotary screw formula compressor that is used for compression refrigerant gas or other fluids generally includes a pair of rotor, and this rotor is arranged on the intermeshing protruding stupefied and groove of its periphery with having spirality.Working fluid enters compressor and enters groove between the rotor from intake section.The rotation of rotor forms the V-arrangement compression chamber, and working fluid is contained in this chamber and along with the outlet of this chamber in the compressor outlet shell moved, the volume-diminished in chamber.When the protruding stupefied top of the rotor in the forward position that limits compression chamber discharged the edge of the liberation port in the shell through compressor, working fluid was discharged from.Thereby provide the metal and the seal compression chamber of oiling agent lubricating contact to rotor.
For the controlled change that volume capacity is provided is controlled compressibility simultaneously, known employing sliding shutter, its whole length direction along it is communicated with the hole of the compressor that rotor wherein is installed.The end of sliding shutter is movably with respect to rotor, and its position is used to control the amount of compressed working fluid, and therefore changes the whole volume of compressor in a controlled manner.The structure of the sliding shutter of rotary screw formula compressor allows to keep unlimited variable capacity, and this has caused very effective compressor load simultaneously.
The position of sliding shutter is by the pressure control in the cylinder, and this pressure acts on the piston that is connected to sliding shutter by axle, and this has just formed sliding valve component together.The rotor of screw compressor is with high speed rotating, and can construct many group rotors and/or compressor is worked together, thereby further improves circuit Fluid Volume in system, thereby improves the operation capacity of system.When rotor provided the continuous sucking action, along with compressed working fluid is released at liberation port, every group rotor and/or compressor produced pressure pulse.Typically, when working fluid left rotor, whole sliding valve component was exposed to release pulses.These release pulses have very high energy and can cause causing to the excessive wear of sliding valve component and the vibration that increases the noise level in the compressor.Especially, pulse sends back sliding shutter from the piston reflection and by axle.
In certain sliding shutter position, the distance from the liberation port to the piston equals half of release pulses acoustics wavelength.When in these position operation, on sliding valve component, produce the resonance that increases the release pulses effect.This causes conversely to sliding valve component, comprises the more quick-wearing of the matching surface of sliding shutter, piston seal bar and sliding valve component and compressor case.These vibrations also are sent to compressor case.
U. S. Patent 5,979,168 disclose a kind of sliding shutter that is used in the screw compressor, and it is by opening the size that a part of volume reduces the volume that is used to compress to suction pressure.This sliding shutter is by from the gas of single source, from the refrigerant gas institute gas-operated of the release pressure side of screw compressor, and this sliding shutter carries out fluid with them and is communicated with.Patent 5,979,168 device comprises sliding valve component, the connecting rod that it has valve part, piston and valve partly is connected to connecting rod.Be discharged from the release gas of compression chamber and enter release channel.Dividing element is arranged in this release channel, and comprises the hole that is penetrated by this connecting rod.This dividing element forms the barrier to the oiling agent that discharges with the gas stream steam, but permission gas passes the hole in the dividing element.As a result, the gas on the either side of hole all is in same pressure, but passes the essentially no oiling agent of gas in hole.Dividing element also comprises weepage holes, thereby the opposite side that may be discharged to dividing element by any minor amounts of lubricants in hole.
Patent 5,979,168 purposes of being explained are to reduce to allow to enter valve with the oiling agent in the gas of operation sliding shutter, but it does not recognize the problem of vibration and acoustic resonance.
U. S. Patent 5,044,894 disclose a kind of double-piston system, are used to regulate the slide stop of sliding shutter and screw compressor.Patent 5,044,894 piston are arranged in the control shell of the piston cavity that forms two separation.Concentric annular bar extends to sliding shutter and slide stop from piston by this control shell.Be applied to piston cavity from the oil of oil separator supply, thereby cause the mobile of piston and cause the variation of sliding shutter and slide stop position.Stamping Steel Ribbon on the bar seals piston cavity each other and piston cavity and release chamber is sealed.Though patent 5,044, two piston systems of 894 think that the use Stamping Steel Ribbon can be isolated the variation in piston and the multichannel release on bar, but it does not recognize the caused problem of energy reflection of passing through sliding valve component from release pulses, comprises acoustic resonance, noise and excessive wear.In addition, owing in piston cavity, introduce oil, patent 5,044, the different mechanical systems that 894 propositions have different resistances and have the different damping characteristic probably, it may not can produce resonance.Consider the problems referred to above, a kind of screw compressor need be provided, it weakens acoustic resonance and reduces compressor case and the wearing and tearing of sliding shutter and minimizing compressor noise level.
Summary of the invention
Therefore, be desirable to provide a kind of screw compressor that overcomes these and other shortcomings of the prior art.Particularly, be desirable to provide such screw compressor, it is provided with sliding valve component, by introducing damping device between piston and the sliding shutter piston being separated with release.More specifically, be desirable to provide such screw compressor, it has the damping device with the compressor case one, and this damping device separates piston and suppress sound, vibration and noise in the compressor with liberation port.
The present invention pays close attention to screw compressor and comprises the compression system of this screw compressor.This screw compressor comprises compressor case, its have with therebetween fluid from the suction side of compressor the passage to the release side flow of compressor, this shell comprises the acoustics barrier of one, be arranged on the paired engagement rotor in this passage, this rotor discharges hydrodynamic pressure that liberation port side on flow by described passage to compressor from the suction port on the compressor suction side in order to increase, and and be arranged on sliding valve component in the compressor case movably, to regulate compressor capacity, this sliding valve component comprises the sliding shutter that is connected to piston by axle, and wherein this piston and sliding shutter are arranged on the opposite side of acoustics barrier.This acoustics barrier comprises that hole, this acoustics barrier that size is fit to hold axle weaken acoustic resonance and noise in the compressor, and this acoustics barrier is arranged on the intended distance place of leaving liberation port.
The present invention also pays close attention to a kind of method that weakens the acoustic resonance in the screw compressor.This method comprises the passage by the compressor case of screw compressor, passes through refrigerant gas through liberation port to the release side of compressor from the suction side of compressor, and the part of passage is limited by a pair of engagement rotor that is arranged in the compressor case passage; The acoustics barrier of setting and compressor case one, this acoustics barrier is positioned at and leaves liberation port intended distance place; Sliding valve component is set in compressor case, and this sliding valve component comprises the sliding shutter that is connected to piston by axle, wherein this pass by with the hole that barrier limited of compressor case one, this sliding shutter and piston are positioned on the opposite side of barrier; And, sliding shutter adjusts flowing of refrigerant gas by passage by being moved to respect to the second place of engagement rotor from the primary importance with respect to the engagement rotor.
The invention has the advantages that, be arranged on the piston of sliding valve component and reduced greatly to discharge the possibility that produces acoustic resonance, because described one barrier has weakened sound and vibration by periodicity from the compression refrigeration gas of compression chamber from the one acoustics barrier between the release of rotor.
Another advantage of the present invention is, is arranged on the piston of sliding valve component and reduced wearing and tearing to sliding valve component from the one acoustics barrier between the release of rotor.
Another advantage of the present invention is, is arranged on the piston of sliding valve component and reduced the noise level of compressor from the acoustics barrier of the one between the release of rotor.
An advantage more of the present invention is, with the manufacturing of the integrally formed acoustics barrier of compressor case a part as the compressor case manufacture process, be reduced in the number of the additional components in the compressor case, reduce may originating of leakage and potential failure, simplify assembling simultaneously.
Other characteristics of the present invention and advantage will become apparent from the description below in conjunction with the preferred embodiment of accompanying drawing, and the mode by example shows principle of the present invention in the accompanying drawings.
Description of drawings
Fig. 1 is the refrigeration system of the one exemplary embodiment according to the present invention;
Fig. 2 is the local amplification view that the sliding valve component of the screw compressor in the refrigeration system of Fig. 1 is shown, and shows the compressor that is positioned at complete load situation;
Fig. 3 is the local amplification view of Fig. 2, and the compressor that is in the complete discharge position is shown;
Fig. 4 is the perspective view of the piston housing parts of compressor case;
Fig. 5 is screw compressor vibration-testing result's diagrammatic representation.
Embodiment
Thereby introducing separates the piston of sliding valve component and sliding shutter part with the compressor case one of screw compressor barrier physically piston with discharge gas separation.Discharge gas and be the pressurized gas that produce as from the gas of the screw rod that is formed on engagement or each discharge a plurality of compression chambers between the rotor.Along with the rotation of one or more rotors, this gas discharges in periodic mode from compression chamber, produces pulse.The frequency of pulse and size depend on a plurality of factors, include but not limited to the rotational speed of rotor and the number that compresses available compression chamber.Therefore, because the position of one barrier, pulse is weakened and less energy is absorbed by piston and reflected back by sliding valve component by axle, therefore reduces the vibratory output in the sliding valve component, and reduces this assembly risk of wearing and tearing too early.Not only vibration or pulse weaken the reduction acoustic resonance, and the distance of point is fixed from the liberation port to the power absorption.That is, present energy is held the barrier that leaves the liberation port fixed range and absorbs, and changes even piston leaves the distance of liberation port and one barrier.Distance by suitable selection from liberation port to the one barrier, the possibility of acoustic resonance is further reduced, because the distance of selecting should be corresponding to the acoustics wavelength that can not cause resonating in normal squeeze operation.
At first with reference to Fig. 1, refrigeration system 10 comprises screw compressor 12, condenser 14, expansion valve (TVX) 16 and the vaporizer 18 that connects successively to allow refrigeration agent to flow betwixt.Compressor 12 comprises compressor case 20, and it comprises the working portion of compressor 12.As shown in Figure 1, compressor case 20 comprises inlet shell 100, rotor case 200, discharges shell 300 and piston shell 400.
Be in and suck or the refrigerant gas of lower pressure is directed to the circulation suction area of the inlet channel on the suction side 105 of compressor 12 from vaporizer 18.Motor is used to drive rotor.Motor can comprise the motor stator of being made up of lamination (laminations) and coil-end (coil heads) 110.This motor also comprises the motor driven 120 that is connected to rotor 210 by live axle 130, and rotor 210 is by intermeshing protruding stupefied and the groove and the second rotor (not shown) fit engagement.This rotor rotates in the cylinder of the accurate machining manufacturing with rotor case 200.Two rotors are not same shapes.But one normally protruding, and another is normally recessed.Normally protruding rotor typically rotates than another normally recessed rotor or rotates sooner.
The refrigeration agent that is in suction pressure flows into the rotor case 200 at suction port 107 places, and enters the compression groove (compression pocket) that is limited between the surface that cooperates rotor.Phase despining and engagement by screw rotor, compression groove is also referred to as lobe (lobes), reduces dimensionally and the coaxial high pressure release side 305 that is set to compressor 12, at this place, compressed refrigerant is released in the release channel 305 that discharges shell 300 subsequently.Compressed refrigeration agent finally is discharged to condenser 14 from compressor 12, and continues by refrigeration cycle.Typically, screw compressor comprises be used for oil separator (not shown) that the oiling agent that compressed refrigeration agent carries is separated from refrigeration agent.In addition, comprise that typically for example the structure of lubrication groove (not shown) is used to store unnecessary oiling agent.
Fig. 2 and 3 illustrates the compressor 12 that is in complete load and complete discharge state respectively better, and compressor 12 comprises the single piston sliding valve component 500 of control compressor 12 capacity.Sliding valve component 500 comprises by axle 530 and being rigidly connected to each other but the sliding shutter 510 and the piston 520 that are oppositely arranged on axle 530.Sliding shutter 510 forms the part on rotor cases 200 borders, and the ability of the load of regulating rotor screw thread (rotor thread) amount that is exposed to suction port and compressor 12 is provided.
Refrigerant compressed gas is from rotor is discharged to release channel on the release side 305 of liberation port 310.Liberation port 310 is made of two-part, by the release terminal 512 of sliding shutter 510 forms as the first portion of radial component 312 and the second portion that forms by release shell 300 as axial component 314.The geometrical shape of compressor case 20 makes the size of radial component 312 by the positioning control of sliding shutter 510.
Thereby regulate sliding valve component 500 and control the position of sliding shutter 510 above rotor by the pressure that is applied to piston 520.Piston 520 is included in size can be held in the piston-cylinder 405 of piston shell 400 of piston 520, piston 520 has one or more Stamping Steel Ribbons 522, make piston 520 will be separated into two different chambeies with the piston-cylinder 405 that the suction side 105 and the release side 305 of compressor are carried out the fluid connection effectively, a chamber is on the either side of piston 520.Although Stamping Steel Ribbon is arranged, providing enough lubricities to make passes through via piston 520 either sides piston 520 on-load pressures, piston 520 is shifted, and therefore, all the other sliding valve components 500 that comprise the sliding shutter 510 that is connected to slide-valve door-hinge 530 opposite ends move, and increase or reduce compressor capacity.
As shown in Figure 3, when sliding shutter 510 unloadings, for example the biasing arrangement of spring 540 is shifted piston 520 onto on the right of cylinder 405.This moves to right sliding shutter 510 successively.In this position, sliding shutter is called as unloaded, thereby and sliding shutter 510 recirculation port 230 that exposes refrigerant gas do not get back to the suction side 105 of compressor 12 with having compression.For the increase capacity, pressure is incorporated into piston-cylinder 405 from discharging side 305 by piston-cylinder opening 420, reacts on spring 540 and mobile piston 520 and therefore sliding shutter 510 is moved to left.Figure 2 illustrates complete load situation.In this position, recirculation port 230 is fully closed.The suction gas of all introducing rotors is compressed now.When sliding shutter 510 during by complete discharge, as shown in Figure 3, recycle sections 230 is opened fully, allow part of refrigerant gas walk around rotor, around motor cycles and get back to the suction side inlet.Under the partial load condition, recycle sections 230 is closed by sliding shutter 510 parts.
In operation, and particularly make compressor 12 only during partial load when regulating sliding valve component 500, the gas of compression from rotor with pulse release, the energy that this pulse is very high typically.As previously mentioned, in the screw compressor design, this can cause vibrating and producing the acoustic resonance that causes sliding valve component 500 heavy wears, comprises the wearing and tearing of the premature failure that can cause compressor 12.
In the present invention, acoustics barrier 410 is introduced into compressor case 20 to reduce pulse to the influence of sliding valve component 500 and overcome undue oscillation and to the problem of the noise level do not expected in the wearing and tearing of assembly 500, the compressor 12, the obvious destruction that causes when also overcoming the acoustic wave appearance coupling when 310 distance and release pulses from piston 520 to liberation port, for example wearing and tearing of sliding valve component 500.In several situations, harmonic effect can be damaged compressor case 20 self.During the casting of compressor case 20, barrier 410 is typically integrally formed with compressor case 20.
Will be understood that the acoustics wavelength is the characteristic of refrigeration agent and can changes under the different operating temperature and pressure.In addition, the frequency that is produced by compressor 12 is based on the design of rotor 210 and the service speed of compressor 12.Therefore; what will be further understood that is; the frequency of the compressor 12 that acoustics wavelength and causing resonates can wide variation; but acoustics barrier 410 can suitably be arranged on the intended distance place of leaving liberation port 310; thereby allow sliding shutter 510 on the whole length of expectation, to move, the pulse of discharging, still protect piston 520 simultaneously from liberation port 310.
The moving to be incorporated in the face of the chamber of the piston-cylinder 405 of biasing arrangement or from this chamber by refrigeration agent of piston 520 discharged and controlled, and piston-cylinder 405 is communicated with the suction side 105 and release side 305 fluids of compressor 12.In order to load compressor 12 and to increase its capacity, pressurized gas are introduced through conduit tube component 425 from the release side 305 of compressor 12 by piston-cylinder opening 420, and this opening serves as the inlet that carries pressurized gas.Conversely, in order to unload compressor 12, gas can remove by piston-cylinder opening 420 to the suction side 105 of compressor 12 by discharge gases through conduit tube component 425, and this opening serves as outlet now.Cylinder opening 420 can be by the control of electromagnetic valve (not shown) as the function of inlet or outlet, and this electromagnetic valve is the canonical dissection of conduit tube component.When needs load compressor, can introduce refrigeration agent by electromagnetic valve by opening 420, this electromagnetic valve makes opening 420 be communicated with release side 305 fluids of compressor 12.Similarly, when decision compressor 12 should be unloaded, can extract refrigeration agent out by electromagnetic valve by opening 420, this electromagnetic valve makes opening be communicated with suction side 105 fluids of compressor 12.This has described known sliding shutter operation.
Preferably, the spring 540 between the end wall 407 that is arranged on piston 520 and is provided by barrier 410 is provided sliding valve component.End wall 407 is preferably as the spring arresting stop.Spring 540 promotes piston 520, thereby remains on the appropriate location when lacking the pressurized gas of introducing by piston-cylinder opening 420, makes that sliding shutter 510 is automatically unloaded when lacking pressurized gas.
The hole 415 that is limited by barrier 410 is near the diameter of axle 530, but has enough tolerances to slide before and after when piston 520 skews to allow axle 530, do not cause the damage to sliding valve component 500 or compressor case 12.Piston 520 is designed and manufactured as and allows piston 520 to be free to slide in piston-cylinder 405, and does not have gas flow around piston 520.Typically, Stamping Steel Ribbon 522 is set to prevent piston 520 gas leakage on every side.So be provided with, piston 520 can be protected from release pulses, and does not need to be arranged on the axle 530 of sliding valve component 500 or be connected to any Stamping Steel Ribbon of compressor case 20 or the sheet of other non-integral.
As mentioned above, acoustics barrier 410 is integral parts of compressor case 20.Preferably, barrier 410 is as the casting of an integral part of the piston housing parts 400 of compressor case 20, though machining also is fine suitable costliness by forging the compressor case 20 that forms.As shown in Figure 4, piston shell 400 is a slice overall structures that formed by iron casting, and it has the engaging surface 402 that is connected to compressor case 20.Piston shell 400 comprises two passages, piston-cylinder 405 and discharge the second channel 430 that forms a part of release channel on the side 305 and compressed refrigeration agent is directed to condenser at compressor.Can find out best that from Fig. 2 and 3 after sliding valve component 500 assemblings, piston end plate of outer cover 404 is connected to piston shell 400.End wall 409 in the face of the piston-cylinder 405 of the end wall 407 that is provided by barrier 410 is provided piston end plate of outer cover 404.By the barrier 410 of manufacturing with compressor case 20 one, energy from release pulses weakens in whole compressor shell 20, reduced damage risk to compressor 12 other working portions, compressor case is normally very big, particularly when when comparing such as the operation element of sliding valve component 500.For example some material of gray cast iron is effective especially to weakening vibration.
The screw compressor with one barrier according to the embodiment of the invention can be used in any compression system, but in using the refrigeration system of the high-density refrigerant of 134a for example is useful especially, this is because its high density, conduct described release pulses easilier, therefore when no barrier, cause more vibrations and galling more at top level more.
Further show the validity of the embodiment of the invention in the indefiniteness example below.
Example
The screw compressor with sliding valve component that does not promptly have the barrier of isolation piston and sliding shutter according to conventional methods compare with screw compressor according to an exemplary embodiment of the present invention, but other aspects of compressor is identical.Two kinds of compressors adopt the 134a refrigeration agent to test as refrigerant gas.Then as the function measurement of various sliding shutters position at the vibration of compressor of 355Hz.In test, each compressor all remains on each sliding shutter position long enough time to realize the operation of steady state.
Shown in the diagram of Fig. 5, it has shown peak force and the load of percentage sliding shutter in the G load, compressor without any barrier between piston and sliding shutter demonstrates quite high G peak, particularly from about percent 10 sliding shutter positions to about 80, wherein percent 100 corresponding to the sliding shutter position of load compressor fully, and percent 0 positions corresponding to the sliding shutter of opening of the maximum recirculation that allows refrigeration agent.Fig. 5 illustrates and vibrates never being reduced to below about 0.2G of the screw compressor (being marked as " wall ") with one barrier above 2G of the screw compressor of barrier (being marked as " initially "), has reduced a whole magnitude.
Though the present invention has been described with reference to preferred embodiment, it should be appreciated by those skilled in the art, can in not break away from category of the present invention, carry out various variations and equivalent and can replace with its element.In addition, can carry out various improvement so that instruction of the present invention adapts to particular condition or material, and not break away from its essential category.Therefore, purpose of the present invention is not limited to disclosed as the specific embodiment of implementing best mode of the present invention, but the present invention will comprise all embodiments that drop in the claims category.
Claims (22)
1, a kind of screw compressor comprises:
Compressor case has passage, with therebetween fluid from the suction side of described compressor to the flowing of the release side of described compressor, described shell comprises the acoustics barrier of one;
Paired engagement rotor is arranged in the described passage, and described rotor is in order to increase the pressure that discharges the fluid of the liberation port on the side from the suction port on the compressor suction side by described channel flow to compressor; With
Sliding valve component, be arranged on movably in the described compressor case, to regulate described compressor capacity, described sliding valve component comprises the sliding shutter that is connected to piston by axle, wherein said piston and sliding shutter are arranged on the opposite side of described acoustics barrier, and wherein said acoustics barrier comprises that size is suitable for holding the hole of described axle, and described acoustics barrier weakens acoustic resonance and the noise in the compressor, and wherein said acoustics barrier is arranged on the intended distance place of leaving liberation port.
2, screw compressor as claimed in claim 1, wherein said piston is arranged in the piston-cylinder, at least a portion of piston-cylinder is limited by described compressor case, described piston-cylinder size is fit to hold piston, and the suction side by conduit tube component and shell and discharge side and carry out fluid and be communicated with.
3, screw compressor as claimed in claim 2, wherein said compressor case comprises cast iron.
4, screw compressor as claimed in claim 2, wherein said sliding valve component comprises single piston.
5, screw compressor as claimed in claim 2, wherein said sliding valve component also comprises biasing arrangement, it to be promoting described piston along first direction, and wherein introduces refrigerant gas the piston-cylinder along promoting piston in the opposite direction with described first party from discharging side by conduit tube component.
6, screw compressor as claimed in claim 2, wherein said compressor case also comprises the piston housing parts, wherein said piston housing parts comprises at least a portion piston-cylinder and at least a portion conduit tube component.
7, screw compressor as claimed in claim 2, wherein said piston-cylinder size is suitable for holding described piston, and making does not have refrigerant gas to pass through boundary leakage between described compressor and the piston basically.
8, screw compressor as claimed in claim 2, wherein said acoustics barrier comprises the end wall of a part of piston-cylinder.
9, screw compressor as claimed in claim 1, wherein said sliding valve component also comprises spring, and it is arranged between described piston and the acoustics barrier, and described spring has the bias voltage of the described piston of promotion away from the acoustics barrier.
10, screw compressor as claimed in claim 1, wherein said compressor case comprise inlet shell, rotor case, release shell and piston shell.
11, a kind of method that reduces the acoustic resonance in the screw compressor comprises the steps:
The passage of the compressor case by screw compressor, from the suction side of described compressor to the release side of compressor by the liberation port refrigerant gas that circulates, the portion of channel that is limited by paired engagement rotor is arranged in the compressor case passage;
The acoustics barrier of setting and described compressor case one, described acoustics barrier is positioned at the intended distance place of leaving described liberation port;
In described compressor case, sliding valve component is set, described sliding valve component comprises the sliding shutter that is connected to piston by axle, wherein said axle pass by with the hole that barrier limited of compressor case one, described sliding shutter and piston are positioned on the opposite side of described barrier; With
By being moved to the second place with respect to the rotor of described engagement from the primary importance with respect to the rotor of described engagement, sliding shutter changes flowing of refrigerant gas by described passage.
12, method as claimed in claim 11, the step of wherein said circulation refrigerant gas comprise circulation 134a refrigerant gas.
13, method as claimed in claim 11, wherein said being used for comprises casting material by the compressor case of compressor case circulation refrigerant gas.
14, method as claimed in claim 11, the step that sliding valve component wherein is set in compressor case comprises:
Sliding valve component is set in compressor case, make piston be arranged on movably in the piston-cylinder of compressor case, therefore described piston-cylinder size is fit to hold piston, and wherein mobile piston causes mobile sliding shutter, changes gas flow and controls the capacity of compressor.
15, method as claimed in claim 14, wherein moving sliding shutter from the primary importance with respect to the rotor of described engagement to the second place is by realizing with respect to the pressure on pressure change piston one side on the piston opposite side.
16, method as claimed in claim 14, wherein a part of compressor case limits the end wall of at least a portion compresser cylinder.
17, method as claimed in claim 16, the part compressor case that wherein limits at least a portion piston-cylinder end wall is the acoustics barrier.
18, method as claimed in claim 14, the step that sliding valve component wherein is set also comprises: the biasing arrangement that promotes piston on the direction of described relatively acoustics barrier.
19, method as claimed in claim 14, wherein from respect to the primary importance of engagement rotor to the sliding shutter of the second place mobile be by from discharge side introduce pressurized gas to the piston-cylinder increasing the pressure of piston one side, thereby along promoting piston in the opposite direction with the first party that promotes by biasing arrangement and realizing.
20, a kind of refrigeration system comprises:
Condenser;
Vaporizer;
Expansion valve; With
Screw compressor comprises compressor case, and described shell has passage, this passage be used to allow therebetween fluid from the suction side of described compressor to the flowing of the release side of described compressor, described shell comprises the acoustics barrier of one; Be arranged on the paired engagement rotor in the described passage, described rotor is in order to increase the pressure that discharges the fluid of the liberation port on the side from the suction port on the compressor suction side by described channel flow to compressor; And sliding valve component, be arranged on movably in the described compressor case, to adjust described compressor capacity, described sliding valve component comprises the sliding shutter that is connected to piston by axle, wherein said piston and sliding shutter are arranged on the opposite side of described acoustics barrier, and wherein said acoustics barrier comprises that size is suitable for holding the hole of described axle, and described acoustics barrier weakens acoustic resonance and the noise in the compressor, and wherein said acoustics barrier is arranged on the intended distance place of leaving liberation port
Wherein said condenser, vaporizer, expansion valve and screw compressor are in turn connected into the passage of refrigeration agent betwixt.
21, refrigeration system as claimed in claim 20, the sliding valve component of wherein said screw compressor comprises single piston.
22, refrigeration system as claimed in claim 20, wherein said refrigeration agent comprises the 134a refrigeration agent.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US11/042,949 | 2005-01-24 | ||
| US11/042,949 US20060165543A1 (en) | 2005-01-24 | 2005-01-24 | Screw compressor acoustic resonance reduction |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1811189A true CN1811189A (en) | 2006-08-02 |
Family
ID=36696934
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2006100060686A Pending CN1811189A (en) | 2005-01-24 | 2006-01-24 | Screw compressor acoustic resonance reduction |
Country Status (2)
| Country | Link |
|---|---|
| US (1) | US20060165543A1 (en) |
| CN (1) | CN1811189A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104696219A (en) * | 2013-12-05 | 2015-06-10 | 珠海格力电器股份有限公司 | Screw compressor spool valve and screw compressor |
| CN113513474A (en) * | 2020-04-09 | 2021-10-19 | 江森自控空调冷冻设备(无锡)有限公司 | Screw compressor, refrigeration system and control method of refrigeration system |
Families Citing this family (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4401408B2 (en) * | 2007-08-30 | 2010-01-20 | 日立アプライアンス株式会社 | Screw compressor capacity control device |
| ES2629981T3 (en) * | 2007-10-01 | 2017-08-17 | Carrier Corporation | Pulsation damper for screw compressor |
| EP2209968B1 (en) * | 2007-10-10 | 2018-01-24 | Carrier Corporation | Slide valve system for a screw compressor |
| CN104314811A (en) * | 2014-09-22 | 2015-01-28 | 珠海格力电器股份有限公司 | Compressor slide valve assembly and refrigeration screw compressor |
| US10704549B2 (en) | 2015-03-31 | 2020-07-07 | Hitachi Industrial Equipment Systems Co., Ltd. | Screw compressor having a discharging passage with enlarged cross section area |
| US9644630B2 (en) * | 2015-07-23 | 2017-05-09 | Fca Us Llc | Supercharger with integrated contraction chamber for noise attenuation |
| EP3334938A1 (en) | 2015-08-11 | 2018-06-20 | Carrier Corporation | Refrigeration compressor fittings |
| US10808969B2 (en) | 2015-08-11 | 2020-10-20 | Carrier Corporation | Screw compressor economizer plenum for pulsation reduction |
| US10941776B2 (en) | 2015-10-02 | 2021-03-09 | Carrier Corporation | Screw compressor resonator arrays |
| CN208089547U (en) * | 2017-09-30 | 2018-11-13 | 江森自控空调冷冻设备(无锡)有限公司 | A kind of guiding valve |
| CN107524599A (en) * | 2017-10-13 | 2017-12-29 | 苏州利森空调制冷有限公司 | Single screw compressor internal volume rate regulating mechanism |
| CN110566461A (en) * | 2019-09-11 | 2019-12-13 | 珠海格力电器股份有限公司 | two-stage compressor, control method of two-stage compressor and air conditioning unit |
Family Cites Families (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1479451A (en) * | 1973-06-18 | 1977-07-13 | Svenska Rotor Maskiner Ab | Meshing screw compressors |
| US4052135A (en) * | 1976-05-11 | 1977-10-04 | Gardner-Denver Company | Control system for helical screw compressor |
| US4575323A (en) * | 1984-05-23 | 1986-03-11 | Kabushiki Kaisha Kobe Seiko Sho | Slide valve type screw compressor |
| US5044894A (en) * | 1990-11-30 | 1991-09-03 | Carrier Corporation | Capacity volume ratio control for twin screw compressors |
| US5183395A (en) * | 1992-03-13 | 1993-02-02 | Vilter Manufacturing Corporation | Compressor slide valve control |
| US5257921A (en) * | 1992-05-19 | 1993-11-02 | Fes, Inc. | Electronic slide valve position indicator |
| JP3254457B2 (en) * | 1992-09-18 | 2002-02-04 | 株式会社日立製作所 | Method for forming rotor of oilless screw compressor and oilless screw compressor using the rotor |
| US5342179A (en) * | 1993-03-05 | 1994-08-30 | Tecumseh Products Company | Compressor shock absorbing mount assembly |
| US5507151A (en) * | 1995-02-16 | 1996-04-16 | American Standard Inc. | Noise reduction in screw compressor-based refrigeration systems |
| US5509273A (en) * | 1995-02-24 | 1996-04-23 | American Standard Inc. | Gas actuated slide valve in a screw compressor |
| DE19533807A1 (en) * | 1995-09-13 | 1997-03-20 | Bosch Gmbh Robert | Fuel injection pump |
| US5997168A (en) * | 1997-04-14 | 1999-12-07 | Electronic Data Systems Corporation | Optimizing the operation of an equipment control system |
| JPH11324919A (en) * | 1998-05-11 | 1999-11-26 | Toyota Autom Loom Works Ltd | Method and device for restraining resonance |
| DE19909689B4 (en) * | 1999-03-05 | 2009-07-23 | Rohs, Ulrich, Dr.-Ing. | Piston engine with continuous combustion |
| DE19935041A1 (en) * | 1999-07-26 | 2001-02-08 | Bitzer Kuehlmaschinenbau Gmbh | Screw compressor |
| US6623262B1 (en) * | 2001-02-09 | 2003-09-23 | Imd Industries, Inc. | Method of reducing system pressure pulsation for positive displacement pumps |
-
2005
- 2005-01-24 US US11/042,949 patent/US20060165543A1/en not_active Abandoned
-
2006
- 2006-01-24 CN CNA2006100060686A patent/CN1811189A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104696219A (en) * | 2013-12-05 | 2015-06-10 | 珠海格力电器股份有限公司 | Screw compressor spool valve and screw compressor |
| CN113513474A (en) * | 2020-04-09 | 2021-10-19 | 江森自控空调冷冻设备(无锡)有限公司 | Screw compressor, refrigeration system and control method of refrigeration system |
| CN113513474B (en) * | 2020-04-09 | 2023-02-21 | 江森自控空调冷冻设备(无锡)有限公司 | Screw compressor, refrigeration system and control method of refrigeration system |
Also Published As
| Publication number | Publication date |
|---|---|
| US20060165543A1 (en) | 2006-07-27 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN1811189A (en) | Screw compressor acoustic resonance reduction | |
| CN1161547C (en) | Compressor | |
| US10527041B2 (en) | Compressor having oil recovery means | |
| JP4946340B2 (en) | Double-head piston compressor | |
| EP0354867A2 (en) | Scroll type compressor | |
| MXPA01001177A (en) | Scroll compressor. | |
| EP1851437B1 (en) | Capacity varying type rotary compressor | |
| US5622487A (en) | Scroll compressor having a separate stationary wrap element secured to a frame | |
| EP2643590B1 (en) | Mounting arrangement for a suction muffler in a linear motor compressor | |
| EP0916847A1 (en) | Compressor housing | |
| KR20060039179A (en) | Compressor | |
| EP1830069A1 (en) | Rotary compressor | |
| EP3450763B1 (en) | Screw compressor | |
| US20040234386A1 (en) | Discharge muffler having an internal pressure relief valve | |
| CN110785566A (en) | Rotary compressor | |
| KR102547593B1 (en) | Variable displacement swash plate type compressor | |
| JP6830159B2 (en) | Oil-free vacuum pumps with prismatic pistons and corresponding compressors | |
| US10968911B2 (en) | Oscillating piston-type compressor | |
| KR100527587B1 (en) | Noise reducing structure of reciprocating compressor | |
| JP3993998B2 (en) | Variable capacity gas compressor | |
| JP2000274384A (en) | Gas compressor | |
| KR100286313B1 (en) | Compressor | |
| KR20210105247A (en) | Compressor | |
| JPH0151918B2 (en) | ||
| JP2006144622A (en) | Gas compressor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
| WD01 | Invention patent application deemed withdrawn after publication |