US20100209280A1 - Screw compressor pulsation damper - Google Patents
Screw compressor pulsation damper Download PDFInfo
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- US20100209280A1 US20100209280A1 US12/678,401 US67840110A US2010209280A1 US 20100209280 A1 US20100209280 A1 US 20100209280A1 US 67840110 A US67840110 A US 67840110A US 2010209280 A1 US2010209280 A1 US 2010209280A1
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- slide valve
- piston
- screw compressor
- piston cylinder
- discharge
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- 230000010349 pulsation Effects 0.000 title claims abstract description 42
- 238000013016 damping Methods 0.000 claims abstract description 47
- 239000012530 fluid Substances 0.000 claims description 6
- 238000007599 discharging Methods 0.000 claims description 3
- 238000000034 method Methods 0.000 claims 4
- 239000003507 refrigerant Substances 0.000 description 52
- 230000000694 effects Effects 0.000 description 8
- 230000013011 mating Effects 0.000 description 3
- 238000001816 cooling Methods 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 230000004888 barrier function Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 239000000284 extract Substances 0.000 description 1
- 238000000605 extraction Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
- 239000010935 stainless steel Substances 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
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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
- F04C28/10—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0021—Systems for the equilibration of forces acting on the pump
- F04C29/0035—Equalization of pressure pulses
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/06—Silencing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
- F04C2270/13—Noise
-
- 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
- F04C2270/14—Pulsations
Definitions
- Screw compressors typically comprise a pair of counter-rotating, mating male and female screws that have an intermeshing plurality of lands and channels, respectively, that narrow from an inlet end to a discharge end such that an effluent working fluid or gas, or some other such working matter, is reduced in volume as it is pushed through the screws.
- the discharged working matter is released in pulses as each mating land and channel pushes a volume of the working matter out of the compressor.
- Each pulse comprises a burst of wave energy that propagates through the working matter and the screw compressor as the working matter leaves the screws.
- the screw compressors are typically turned, by motors operating at speeds such that the wave pulsations are discharged at a high frequency.
- the pulsations not only produce vibration of the screw compressor, but also produce noise that is amplified by the working matter and the compressor. Such vibration is undesirable as it wears components of the compressor and produces additional noise as the compressor vibrates. Noise from the discharging working matter and vibrating compressor is undesirable as it results in loud operating environments.
- Previous attempts to counteract these problems have involved mufflers, padded mounts and clamps that are mounted external to the screw compressor. These solutions do not address the underlying source of the noise and vibration and only provide after-the-fact countermeasures. In addition to adding cost and weight, such solutions provide only limited noise reduction and do not prevent wear on internal screw compressor components.
- Other solutions have proposed acoustic barriers that prevent pulsation damage to screw compressor components, but do not attenuate screw compressor noise or vibration. There is, therefore, a need for screw compressors having reduced effects from discharge pulsations.
- Exemplary embodiments of the invention include a screw compressor comprising a housing, a slide valve assembly and a pulsation damper.
- the housing receives a supply of working matter from a pair of intermeshing screw rotors, and comprises a slide recess, a pressure pocket, and a piston cylinder.
- the slide valve assembly regulates the capacity of the screw compressor, and comprises a slide valve axially movable within the slide recess and the pressure pocket, a piston head axially movable within the piston cylinder, and a piston shaft connecting the slide valve with the piston head.
- the pulsation damper comprises a flange for separating the pressure pocket from the piston cylinder, a bore for receiving the piston rod, and a damping channel extending through the flange for damping pressure pulsations in the working matter discharged from the pair of intermeshing screw rotors.
- FIG. 1 shows a partially cutaway perspective view of a screw compressor in which the pulsation damper of the present invention is used.
- FIG. 2 shows a schematic diagram of the screw compressor of FIG. 1 showing an outlet case incorporating the pulsation damper.
- FIG. 3 shows a partially cutaway perspective view of the outlet case of FIG. 2 showing a plurality of damping channels comprising the pulsation damper.
- FIG. 1 shows a partially cutaway perspective view of screw compressor 10 , which compresses a working fluid or gas such as a refrigerant that is typically used in refrigeration or air conditioning systems.
- Screw compressor 10 includes rotor case 12 , outlet case 14 , slide case 16 , male screw rotor 18 , female screw rotor 20 , drive motor 22 and slide valve assembly 23 .
- Male screw rotor 18 and female screw rotor 20 are disposed within rotor case 12 and include shafting and bearings such that they can be rotationally driven by drive motor 22 .
- male screw rotor 18 includes shaft 24 A (which extends axially through rotor case 12 and into motor 22 and rests on bearing 26 A), and shaft 24 B (which extends axially into outlet case 14 and rests in bearing 26 B).
- Refrigerant is introduced into rotor case 12 at suction port 28 , directed around motor 22 and into suction pocket 30 at the inlet of screw rotors 18 and 20 .
- Male screw rotor 18 and female screw rotor 20 include meshing grooves and lands that form helical flow paths having decreasing cross sectional areas as the grooves and lands extend from suction pocket 30 .
- the refrigerant is reduced in volume and pressurized as the refrigerant is directed into discharge pocket 32 by screw rotors 18 and 20 , before being discharged at pressure port 34 and released to, for example, a condenser or evaporator of a cooling system.
- Slide valve assembly 23 which includes slide valve 36 , piston rod 38 , piston head 40 and spring assist 42 , regulates the discharge capacity of screw compressor 10 .
- piston head 38 , piston rod 40 and spring assist 42 through a control system, translate slide valve 36 axially between rotors 18 and 20 to vary the volume of refrigerant compressed in the helical flow paths.
- outlet case 14 includes a pulsation damper that mitigates the pulsation effects of the discharged refrigerant.
- screw compressor 10 comprises a two-screw compressor.
- the present invention is readily applicable to compressors having three, four our more screw rotors that employ a reciprocating slide valve system.
- FIG. 2 shows a schematic diagram of screw compressor 10 of FIG. 1 , having pulsation damping means of the present invention.
- outlet case 14 includes damping channels 46 A and 46 B that attenuate the pulsation effects of refrigerant R within screw compressor 10 .
- Screw compressor 10 also includes rotor case 12 , slide case 16 , female screw rotor 20 , drive motor 22 , slide valve assembly 23 (including slide valve 36 , piston rod 38 , piston head 40 and spring assist 42 ) and control system 48 .
- Rotor case 12 includes slide recess 51 , slide stop 52 and recirculation passage 53 .
- Slide case 16 includes piston cylinder 54
- outlet case 14 includes rod flange 58 .
- rotor case 12 , outlet case 14 and slide case 16 comprise a sealed flow path for directing refrigerant R through screw compressor 10 .
- Refrigerant R is directed into rotor case 12 at suction port 28 , and routed around motor 22 to suction pocket 30 .
- Refrigerant R from suction pocket 30 is compressed by male screw rotor 18 (not shown) and female screw rotor 20 and discharged into pressure pocket 32 .
- Female screw rotor 20 includes screw channels, or grooves, 50 A- 50 D that mesh with mating lands or lobes on male screw rotor 18 to form a sealed, decreasing-volume flow path.
- the sealed flow path decreases in volume such that refrigerant R is pushed and compressed as it moves from suction pocket 30 to discharge pocket 32 . Accordingly, refrigerant R enters, for example, screw channel 50 A at suction pocket 30 having pressure P 1 and is discharged from the same screw channel 50 A at discharge pocket 32 having elevated pressure P 2 . Thus, each screw channel delivers a small volume of refrigerant R to discharge pocket 32 . As screw rotors 18 and 20 rotate, a series of discharge pulses of refrigerant R is released to discharge pocket 32 , which causes undesirable noise and vibration of screw compressor 10 .
- Outlet case 14 includes damping channels 46 A and 46 B, which act as pulsation dampers to reduce the noise and vibration effects of refrigerant R as it is discharged from screw rotors 18 and 20 .
- Outlet case 14 which includes discharge pocket 32 , is disposed between rotor case 12 and slide case 16 such that it receives the high pressure side of screw rotors 18 and 20 at a first end, and piston rod 38 of slide assembly 23 at a second end.
- Slide valve 36 of slide assembly 23 is positioned within slide recess 51 of rotor case 12 such that it is disposed between male screw rotor 18 and female screw rotor 20 .
- Slide valve 36 is connected with piston rod 38 and piston head 40 such that slide valve 36 can be axially withdrawn from slide recess 51 and extended into pressure pocket 32 to control the amount of pressurized refrigerant R entrained within screw channels 50 A- 50 D.
- slide valve 36 can be extended to the fully-loaded position (to the left in FIG.
- screw compressor 10 is maximized by maximizing the amount of refrigerant R compressed in the lands and grooves of screw rotors 18 and 20 . From the fully-loaded position, slide valve 36 is moved toward discharge pocket 32 (to the right in FIG. 1 ) to open recirculation passage 53 , decreasing the discharge capacity of screw compressor 10 .
- Piston rod 38 extends through rod flange 58 to connect slide valve 36 within rotor case 12 to piston head 40 disposed within piston cylinder 54 of slide case 16 .
- Piston head 40 includes first pressure side 56 A, which is exposed to refrigerant R at pressure P 2 , and second pressure side 56 B, which is exposed to control oil at pressure P 3 .
- Pressure P 2 is dictated by refrigerant R and screw rotors 18 and 20
- pressure P 3 is regulated by control system 48 .
- control system 48 Based on the loading (i.e. cooling demands) of the refrigerator or air conditioner to which screw compressor 10 is connected, control system 48 , which comprises switches, valves, solenoids and the like, selectively provides control oil to piston cylinder 54 .
- Control oil is admitted into piston cylinder 48 to increase pressure P 3 to exert a force on second pressure side 56 B to move slide valve 36 toward slide stop 52 within slide recess 51 .
- Pressure P 3 is reduced by removing control oil from piston cylinder 54 such that slide valve 36 can be withdrawn from slide recess 51 .
- Spring assist 42 pushes on first pressure side 56 A to assist in withdrawing slide valve 36 from slide recess 51 .
- Piston head 40 is also in contact with refrigerant R, which exerts pressure P 2 on first pressure side 56 A to push piston head 40 away from rod flange 58 .
- Refrigerant R is admitted into piston cylinder 54 through damping channels 46 A and 46 B disposed within rod flange 58 .
- Damping channels 46 A and 46 B, piston cylinder 54 and rod flange 58 are configured to attenuate vibration and noise associated with the discharge of refrigerant R from screw rotors 18 and 20 .
- damping channels 46 A and 46 B act in concert with piston cylinder 54 to provide a Helmholtz resonator to absorb energy from the discharged pulses of refrigerant R.
- FIG. 3 shows a partially cutaway perspective view of slide valve assembly 23 of FIG. 2 , in which damping channels 46 A- 46 C of rod flange 58 are shown.
- Slide valve assembly 23 also includes slide valve 36 , piston rod 38 , piston head 40 and spring assist 42 , which is omitted in FIG. 3 for clarity.
- Slide valve assembly 23 extends axially through rotor case 12 , outlet case 14 and slide case 16 along an actuation path defined by slide recess 51 , pressure pocket 32 and piston cylinder 54 .
- Outlet case 14 is positioned within screw compressor 10 such that first end A connects with rotor case 12 , and second end B connects with slide case 16 .
- Slide valve 36 extends from slide recess 51 in rotor case 12 where it is disposed between rotor screws 18 and 20 , and into pressure pocket 32 within outlet case 14 .
- Piston rod 38 extends axially from slide valve 36 through central bore 60 in rod flange 58 of outlet case 14 , and into piston cylinder 54 of slide case 16 where rod 38 connects with piston head 40 .
- Rod flange 58 comprises a collar positioned on second end B of outlet case 14 such that central bore 60 axially aligns with slide recess 51 (in which slide valve 36 translates within rotor case 12 ) and piston cylinder 54 (in which piston head 40 translates within slide case 16 ).
- rod flange 58 is integrally cast or formed with outlet case 14 along second end B.
- Rod flange 58 separates piston cylinder 54 from slide recess 51 and pressure pocket 32 to form two separate chambers for refrigerant R.
- Rod flange 58 is provided with seal or bearing ring 62 and is attached to rod flange 58 with snap rings 64 A and 64 B, which are disposed within grooves in ring 62 .
- ring 62 comprises a seal and prevents refrigerant R from entering piston cylinder 54 between piston rod 38 and rod flange 58 at bore 60 .
- seal ring 62 comprises a bearing that assists in sliding of piston rod 38 though rod flange 58 as well as performing sealing functions. Damping channels 46 A- 46 C, however, permit refrigerant R to enter piston cylinder 54 within slide case 16 .
- Slide case 16 comprises piston cylinder 54 , which forms an annular extension of outlet case 14 to accommodate piston rod 38 and piston head 40 .
- Piston head 40 divides piston cylinder 54 into discharge side 54 A and control side 54 B.
- Piston head 40 includes seal 65 to prevent flow of control oil and refrigerant R past piston head 40 .
- Piston cylinder 54 therefore, comprises a sealed canister for actuating piston head 40 .
- Discharge side 54 A of this sealed canister also acts as a resonance chamber, that along with damping channels 46 A- 46 C, absorb some of the vibrational and acoustical effects of the pulsed discharges of refrigerant R.
- slide valve assembly 23 is connected with control system 48 ( FIG. 2 ) to actuate the position of slide valve 36 along rotor screws 18 and 20 .
- Slide valve 36 is translated to regulate the discharge capacity of refrigerant R from screw rotors 18 and 20 .
- Control system 48 regulates flow of the control oil into control side 54 B of piston cylinder 54 to vary pressure P 3 .
- Refrigerant R flows into damping channels 46 A- 46 C into piston cylinder 54 within slide case 16 to pressurize discharge side 54 A of piston cylinder 54 to pressure P 2 .
- Refrigerant R is compressed to pressure P 2 between screw rotors 18 and released in pulsed discharges into pressure pocket 32 at slide valve 36 as screw rotors 18 and 20 counter-rotate to open and close the helical flow paths formed by the lobes and channels.
- the pulsed discharges of refrigerant R flow past rod flange 58 before being discharged from screw compressor 10 at pressure port 34 ( FIG. 1 ).
- Damping channels 46 A- 46 C extend through rod flange 58 and permit refrigerant R to enter and pressurize piston cylinder 54 to pressure P 2 .
- rod flange 50 includes four damping channels: damping channels 46 A- 46 C, each disposed in a quadrant of rod flange 50 , and a fourth damping channel omitted due to the section taken out of FIG. 3 .
- Damping channels 46 A- 46 C comprise hollowed-out chambers extending through rod flange 58 of outlet case 14 .
- the lengths of damping channels 46 A- 46 C are determined by the thickness of rod flange 58 , but can be altered by inserting hollow damping tubes 66 A- 66 C into damping channels 46 A- 46 C. Damping tubes 66 A- 66 C are inserted into damping channels 46 A- 46 C such that they extend into piston cylinder 54 and into pressure pocket 32 .
- damping tube 66 A is inserted into damping channel 46 A, and damping tube 66 B is inserted into damping channel 46 B.
- damping tubes 66 A- 66 C each having the same length and the same diameter.
- damping tubes 66 A- 660 comprise stainless steel tubes press fit into damping channels 46 A- 46 C.
- the specific quantity and geometry of damping channels 46 A- 46 C and damping tubes 66 A- 66 C is selected to dampen the acoustic and vibrational pulsation effects of refrigerant R, and can thus vary depending on the specific design parameters of screw compressor 10 .
- the number, length and diameter of damping tubes 66 A- 66 C are selected to extract the maximum amount of energy from refrigerant R as refrigerant R travels through tubes 66 A- 66 C into the resonance chamber formed by discharge side 54 A.
- Refrigerant R is discharged from screw rotors 18 and 20 in pulses at regular intervals having a frequency dictated by the speed at which motor 22 drives screw rotors 18 and 20 . These pulses therefore produce undesirable sound waves that increase the noise generated by screw compressor 10 . The energy contained in these sound waves, however, can be used to do work to attenuate the propagation of the sound waves from screw compressor 10 .
- Outlet case 14 and slide case 16 are configured to function as a Helmholtz resonator, which comprises a container of fluid or gas having a necked opening, such as is produced by discharge side 54 A, refrigerant R and channels 46 A- 46 C.
- a Helmholtz resonator utilizes the spring-like compressibility of the fluid or gas to extract energy from a wave oscillating at a given frequency.
- Refrigerant R fills discharge side 54 A such that additional refrigerant attempting to enter discharge side 54 A through channels 46 A- 46 C must compress the volume of refrigerant R already present within discharge side 54 A.
- a pulsed wave of refrigerant R attempting to enter discharge side 54 A compresses refrigerant R until the crest of the wave is reached. Then, the pressurized refrigerant R within discharge side 54 A will push back as the wave dissipates to the trough.
- the pressurized refrigerant R within discharge side 54 A continues to compress and decompress, thus extracting energy from refrigerant R discharged from screw rotors 18 and 20 .
- the energy extraction reduces the amplitude of the pulsation wave, thereby reducing noise and vibration generated by the pulsed discharges of refrigerant R.
- a Helmholtz resonator extracts the maximum amount of energy from the fluid or gas when the frequency of the wave matches the natural or resonance frequency of the Helmholtz resonator.
- the resonance frequency of the Helmholtz resonator produced by discharge side 54 A and damping channels 46 A- 46 C can be configured to match that of the pulsation discharges of refrigerant R as produced by motor 22 .
- Equation (1) illustrates the resonance frequency of an elongate tube used in a Helmholtz resonator, where f R is the resonance frequency of the tube, v is the speed of sound in the medium filling the tube, A 0 is the area of the tube, L is the length of the tube and V 0 is the volume of resonance chamber.
- the tube or “necked opening” of the Helmholtz resonator comprises the aggregate of tubes 66 A- 66 C.
- f R is the resonance frequency of tubes 66 A- 66 C
- v is the speed of sound in refrigerant R
- a 0 is the total cross-sectional area of tubes 66 A- 66 C
- L is the length of one of tubes 66 A- 66 C
- V 0 is the volume of discharge side 54 A.
- the dimensions of tubes 66 A- 66 C are selected such that the frequency of the discharge pulses of refrigerant R from screw rotors 18 and 20 at a given capacity matches the resonance frequency of the tubes.
- screw compressor 10 is configured to operate at 3,600 RPM at full load.
- Volume V 0 therefore, comprises the volume of discharge side 54 A when piston head 40 is furthest away from rod flange 50 (all the way to the left in FIG. 3 ), and frequency f R is 60 Hz.
- the areas and lengths of tubes 66 A- 66 C are selected based on other design requirements, such as dimensional constraints of rod flange 58 and slide case 16 .
- the number of tubes can be selected based on specific design considerations. In the embodiment shown, tubes 66 A- 66 C have the same lengths and diameters.
- screw compressor 10 is provided with a pulsation damper that is configured for damping pulsation effects of refrigerant R at a specific operating condition.
- tubes 66 A- 66 C can have different geometries, such as different lengths and/or different diameters, such that the pulsation damper is tuned to one specific resonance frequency, or can attenuate vibration and acoustic effects over a range of frequencies.
- rod flange 58 comprises a circular disk or annular ring that can be bolted or otherwise secured to piston cylinder 54 within slide case 16 such that pulsation dampers configured for different resonance frequencies can be interchangeably installed into screw compressor 10 .
Abstract
A screw compressor (10) comprises a housing (12, 14, 16), a slide valve assembly (23) and a pulsation damper. The housing (12, 14, 16) receives a supply of working matter from a pair of intermeshing screw rotors (18, 20), and comprises a slide recess (51), a pressure pocket (32), and a piston cylinder (54). The slide valve assembly (23) regulates the capacity of the screw compressor (10), and comprises a slide valve (36) axially movable within the slide recess (51) and the pressure pocket (32), a piston head (40) axially movable within the piston cylinder (54), and a piston shaft (38) connecting the slide valve (36) with the piston head (40). The pulsation damper comprises a flange (58) for separating the pressure pocket (32) from the piston cylinder (54), a bore (60) for receiving the piston rod (38), and a damping channel (46A) extending through the flange (58).
Description
- The present invention relates generally to screw compressors. Screw compressors typically comprise a pair of counter-rotating, mating male and female screws that have an intermeshing plurality of lands and channels, respectively, that narrow from an inlet end to a discharge end such that an effluent working fluid or gas, or some other such working matter, is reduced in volume as it is pushed through the screws. The discharged working matter is released in pulses as each mating land and channel pushes a volume of the working matter out of the compressor. Each pulse comprises a burst of wave energy that propagates through the working matter and the screw compressor as the working matter leaves the screws. The screw compressors are typically turned, by motors operating at speeds such that the wave pulsations are discharged at a high frequency. The pulsations not only produce vibration of the screw compressor, but also produce noise that is amplified by the working matter and the compressor. Such vibration is undesirable as it wears components of the compressor and produces additional noise as the compressor vibrates. Noise from the discharging working matter and vibrating compressor is undesirable as it results in loud operating environments. Previous attempts to counteract these problems have involved mufflers, padded mounts and clamps that are mounted external to the screw compressor. These solutions do not address the underlying source of the noise and vibration and only provide after-the-fact countermeasures. In addition to adding cost and weight, such solutions provide only limited noise reduction and do not prevent wear on internal screw compressor components. Other solutions have proposed acoustic barriers that prevent pulsation damage to screw compressor components, but do not attenuate screw compressor noise or vibration. There is, therefore, a need for screw compressors having reduced effects from discharge pulsations.
- Exemplary embodiments of the invention include a screw compressor comprising a housing, a slide valve assembly and a pulsation damper. The housing receives a supply of working matter from a pair of intermeshing screw rotors, and comprises a slide recess, a pressure pocket, and a piston cylinder. The slide valve assembly regulates the capacity of the screw compressor, and comprises a slide valve axially movable within the slide recess and the pressure pocket, a piston head axially movable within the piston cylinder, and a piston shaft connecting the slide valve with the piston head. The pulsation damper comprises a flange for separating the pressure pocket from the piston cylinder, a bore for receiving the piston rod, and a damping channel extending through the flange for damping pressure pulsations in the working matter discharged from the pair of intermeshing screw rotors.
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FIG. 1 shows a partially cutaway perspective view of a screw compressor in which the pulsation damper of the present invention is used. -
FIG. 2 shows a schematic diagram of the screw compressor ofFIG. 1 showing an outlet case incorporating the pulsation damper. -
FIG. 3 shows a partially cutaway perspective view of the outlet case ofFIG. 2 showing a plurality of damping channels comprising the pulsation damper. -
FIG. 1 shows a partially cutaway perspective view ofscrew compressor 10, which compresses a working fluid or gas such as a refrigerant that is typically used in refrigeration or air conditioning systems.Screw compressor 10 includesrotor case 12,outlet case 14,slide case 16,male screw rotor 18,female screw rotor 20,drive motor 22 andslide valve assembly 23.Male screw rotor 18 andfemale screw rotor 20 are disposed withinrotor case 12 and include shafting and bearings such that they can be rotationally driven bydrive motor 22. For example,male screw rotor 18 includesshaft 24A (which extends axially throughrotor case 12 and intomotor 22 and rests on bearing 26A), andshaft 24B (which extends axially intooutlet case 14 and rests in bearing 26B). Refrigerant is introduced intorotor case 12 atsuction port 28, directed aroundmotor 22 and intosuction pocket 30 at the inlet ofscrew rotors Male screw rotor 18 andfemale screw rotor 20 include meshing grooves and lands that form helical flow paths having decreasing cross sectional areas as the grooves and lands extend fromsuction pocket 30. Thus, the refrigerant is reduced in volume and pressurized as the refrigerant is directed intodischarge pocket 32 byscrew rotors pressure port 34 and released to, for example, a condenser or evaporator of a cooling system.Slide valve assembly 23, which includesslide valve 36,piston rod 38,piston head 40 andspring assist 42, regulates the discharge capacity ofscrew compressor 10. In particular,piston head 38,piston rod 40 andspring assist 42, through a control system, translateslide valve 36 axially betweenrotors motor 22 drivesscrew rotors pressure pocket 32 in a series of high frequency pulsations, which effectuates undesirable noise and vibration.Outlet case 14 includes a pulsation damper that mitigates the pulsation effects of the discharged refrigerant. In the embodiment shown,screw compressor 10 comprises a two-screw compressor. However, in other embodiments, the present invention is readily applicable to compressors having three, four our more screw rotors that employ a reciprocating slide valve system. -
FIG. 2 shows a schematic diagram ofscrew compressor 10 ofFIG. 1 , having pulsation damping means of the present invention. In particular,outlet case 14 includesdamping channels screw compressor 10.Screw compressor 10 also includesrotor case 12,slide case 16,female screw rotor 20,drive motor 22, slide valve assembly 23 (includingslide valve 36,piston rod 38,piston head 40 and spring assist 42) andcontrol system 48.Rotor case 12 includesslide recess 51,slide stop 52 andrecirculation passage 53.Slide case 16 includespiston cylinder 54, andoutlet case 14 includesrod flange 58. Together,rotor case 12,outlet case 14 andslide case 16 comprise a sealed flow path for directing refrigerant R throughscrew compressor 10. Refrigerant R is directed intorotor case 12 atsuction port 28, and routed aroundmotor 22 tosuction pocket 30. Refrigerant R fromsuction pocket 30 is compressed by male screw rotor 18 (not shown) andfemale screw rotor 20 and discharged intopressure pocket 32.Female screw rotor 20 includes screw channels, or grooves, 50A-50D that mesh with mating lands or lobes onmale screw rotor 18 to form a sealed, decreasing-volume flow path. The sealed flow path decreases in volume such that refrigerant R is pushed and compressed as it moves fromsuction pocket 30 to dischargepocket 32. Accordingly, refrigerant R enters, for example,screw channel 50A atsuction pocket 30 having pressure P1 and is discharged from thesame screw channel 50A atdischarge pocket 32 having elevated pressure P2. Thus, each screw channel delivers a small volume of refrigerant R to dischargepocket 32. Asscrew rotors pocket 32, which causes undesirable noise and vibration ofscrew compressor 10.Outlet case 14 includesdamping channels screw rotors -
Outlet case 14, which includesdischarge pocket 32, is disposed betweenrotor case 12 andslide case 16 such that it receives the high pressure side ofscrew rotors piston rod 38 ofslide assembly 23 at a second end.Slide valve 36 ofslide assembly 23 is positioned withinslide recess 51 ofrotor case 12 such that it is disposed betweenmale screw rotor 18 andfemale screw rotor 20.Slide valve 36 is connected withpiston rod 38 andpiston head 40 such thatslide valve 36 can be axially withdrawn fromslide recess 51 and extended intopressure pocket 32 to control the amount of pressurized refrigerant R entrained withinscrew channels 50A-50D. For example,slide valve 36 can be extended to the fully-loaded position (to the left inFIG. 1 ) such that it abuts slidestop 52 and contacts the entire length ofscrew rotors screw compressor 10 is maximized by maximizing the amount of refrigerant R compressed in the lands and grooves ofscrew rotors slide valve 36 is moved toward discharge pocket 32 (to the right inFIG. 1 ) to openrecirculation passage 53, decreasing the discharge capacity ofscrew compressor 10. - Piston
rod 38 extends throughrod flange 58 to connectslide valve 36 withinrotor case 12 topiston head 40 disposed withinpiston cylinder 54 ofslide case 16. Pistonhead 40 includesfirst pressure side 56A, which is exposed to refrigerant R at pressure P2, andsecond pressure side 56B, which is exposed to control oil at pressure P3. Pressure P2 is dictated by refrigerant R andscrew rotors control system 48. Based on the loading (i.e. cooling demands) of the refrigerator or air conditioner to whichscrew compressor 10 is connected,control system 48, which comprises switches, valves, solenoids and the like, selectively provides control oil topiston cylinder 54. Control oil is admitted intopiston cylinder 48 to increase pressure P3 to exert a force onsecond pressure side 56B to moveslide valve 36 towardslide stop 52 withinslide recess 51. Pressure P3 is reduced by removing control oil frompiston cylinder 54 such thatslide valve 36 can be withdrawn fromslide recess 51.Spring assist 42 pushes onfirst pressure side 56A to assist in withdrawingslide valve 36 fromslide recess 51. Pistonhead 40 is also in contact with refrigerant R, which exerts pressure P2 onfirst pressure side 56A to pushpiston head 40 away fromrod flange 58. Refrigerant R, is admitted intopiston cylinder 54 throughdamping channels rod flange 58.Damping channels piston cylinder 54 androd flange 58 are configured to attenuate vibration and noise associated with the discharge of refrigerant R fromscrew rotors channels piston cylinder 54 to provide a Helmholtz resonator to absorb energy from the discharged pulses of refrigerant R. -
FIG. 3 shows a partially cutaway perspective view ofslide valve assembly 23 ofFIG. 2 , in which dampingchannels 46A-46C ofrod flange 58 are shown.Slide valve assembly 23 also includesslide valve 36,piston rod 38,piston head 40 and spring assist 42, which is omitted inFIG. 3 for clarity.Slide valve assembly 23 extends axially throughrotor case 12,outlet case 14 andslide case 16 along an actuation path defined byslide recess 51,pressure pocket 32 andpiston cylinder 54.Outlet case 14 is positioned withinscrew compressor 10 such that first end A connects withrotor case 12, and second end B connects withslide case 16.Slide valve 36 extends fromslide recess 51 inrotor case 12 where it is disposed between rotor screws 18 and 20, and intopressure pocket 32 withinoutlet case 14.Piston rod 38 extends axially fromslide valve 36 throughcentral bore 60 inrod flange 58 ofoutlet case 14, and intopiston cylinder 54 ofslide case 16 whererod 38 connects withpiston head 40. -
Rod flange 58 comprises a collar positioned on second end B ofoutlet case 14 such thatcentral bore 60 axially aligns with slide recess 51 (in which slidevalve 36 translates within rotor case 12) and piston cylinder 54 (in whichpiston head 40 translates within slide case 16). In the embodiment shown,rod flange 58 is integrally cast or formed withoutlet case 14 along second endB. Rod flange 58separates piston cylinder 54 fromslide recess 51 andpressure pocket 32 to form two separate chambers for refrigerantR. Rod flange 58 is provided with seal or bearingring 62 and is attached torod flange 58 withsnap rings ring 62. In one embodiment,ring 62 comprises a seal and prevents refrigerant R from enteringpiston cylinder 54 betweenpiston rod 38 androd flange 58 atbore 60. In another embodiment,seal ring 62 comprises a bearing that assists in sliding ofpiston rod 38 thoughrod flange 58 as well as performing sealing functions. Dampingchannels 46A-46C, however, permit refrigerant R to enterpiston cylinder 54 withinslide case 16. -
Slide case 16 comprisespiston cylinder 54, which forms an annular extension ofoutlet case 14 to accommodatepiston rod 38 andpiston head 40.Piston head 40 dividespiston cylinder 54 intodischarge side 54A andcontrol side 54B.Piston head 40 includesseal 65 to prevent flow of control oil and refrigerant Rpast piston head 40.Piston cylinder 54, therefore, comprises a sealed canister for actuatingpiston head 40.Discharge side 54A of this sealed canister, however, also acts as a resonance chamber, that along with dampingchannels 46A-46C, absorb some of the vibrational and acoustical effects of the pulsed discharges of refrigerant R. - As explained above,
slide valve assembly 23 is connected with control system 48 (FIG. 2 ) to actuate the position ofslide valve 36 along rotor screws 18 and 20.Slide valve 36 is translated to regulate the discharge capacity of refrigerant R fromscrew rotors Control system 48 regulates flow of the control oil intocontrol side 54B ofpiston cylinder 54 to vary pressure P3. Refrigerant R flows into dampingchannels 46A-46C intopiston cylinder 54 withinslide case 16 to pressurizedischarge side 54A ofpiston cylinder 54 to pressure P2. Refrigerant R is compressed to pressure P2 betweenscrew rotors 18 and released in pulsed discharges intopressure pocket 32 atslide valve 36 asscrew rotors rod flange 58 before being discharged fromscrew compressor 10 at pressure port 34 (FIG. 1 ). Dampingchannels 46A-46C extend throughrod flange 58 and permit refrigerant R to enter and pressurizepiston cylinder 54 to pressure P2. - In the embodiment shown in
FIG. 3 , rod flange 50 includes four damping channels: dampingchannels 46A-46C, each disposed in a quadrant of rod flange 50, and a fourth damping channel omitted due to the section taken out ofFIG. 3 . Dampingchannels 46A-46C comprise hollowed-out chambers extending throughrod flange 58 ofoutlet case 14. The lengths of dampingchannels 46A-46C are determined by the thickness ofrod flange 58, but can be altered by inserting hollow dampingtubes 66A-66C into dampingchannels 46A-46C. Dampingtubes 66A-66C are inserted into dampingchannels 46A-46C such that they extend intopiston cylinder 54 and intopressure pocket 32. As is illustrated inFIG. 3 , dampingtube 66A is inserted into dampingchannel 46A, and dampingtube 66B is inserted into dampingchannel 46B. In the embodiment shown, dampingtubes 66A-66C each having the same length and the same diameter. In one embodiment, dampingtubes 66A-660 comprise stainless steel tubes press fit into dampingchannels 46A-46C. The specific quantity and geometry of dampingchannels 46A-46C and dampingtubes 66A-66C, however, is selected to dampen the acoustic and vibrational pulsation effects of refrigerant R, and can thus vary depending on the specific design parameters ofscrew compressor 10. Specifically, the number, length and diameter of dampingtubes 66A-66C are selected to extract the maximum amount of energy from refrigerant R as refrigerant R travels throughtubes 66A-66C into the resonance chamber formed bydischarge side 54A. - Refrigerant R is discharged from
screw rotors rotors screw compressor 10. The energy contained in these sound waves, however, can be used to do work to attenuate the propagation of the sound waves fromscrew compressor 10.Outlet case 14 andslide case 16 are configured to function as a Helmholtz resonator, which comprises a container of fluid or gas having a necked opening, such as is produced bydischarge side 54A, refrigerant R andchannels 46A-46C. A Helmholtz resonator utilizes the spring-like compressibility of the fluid or gas to extract energy from a wave oscillating at a given frequency. Refrigerant R fillsdischarge side 54A such that additional refrigerant attempting to enterdischarge side 54A throughchannels 46A-46C must compress the volume of refrigerant R already present withindischarge side 54A. Thus, a pulsed wave of refrigerant R attempting to enterdischarge side 54A, compresses refrigerant R until the crest of the wave is reached. Then, the pressurized refrigerant R withindischarge side 54A will push back as the wave dissipates to the trough. As the pulsed wave propagates through crests and waves, the pressurized refrigerant R withindischarge side 54A continues to compress and decompress, thus extracting energy from refrigerant R discharged fromscrew rotors - A Helmholtz resonator extracts the maximum amount of energy from the fluid or gas when the frequency of the wave matches the natural or resonance frequency of the Helmholtz resonator. Thus, the resonance frequency of the Helmholtz resonator produced by
discharge side 54A and dampingchannels 46A-46C can be configured to match that of the pulsation discharges of refrigerant R as produced bymotor 22. Equation (1) illustrates the resonance frequency of an elongate tube used in a Helmholtz resonator, where fR is the resonance frequency of the tube, v is the speed of sound in the medium filling the tube, A0 is the area of the tube, L is the length of the tube and V0 is the volume of resonance chamber. -
- For the present invention, the tube or “necked opening” of the Helmholtz resonator comprises the aggregate of
tubes 66A-66C. Applying this equation to the embodiment of the present invention shown inFIG. 3 , fR is the resonance frequency oftubes 66A-66C, v is the speed of sound in refrigerant R, A0 is the total cross-sectional area oftubes 66A-66C, L is the length of one oftubes 66A-66C, and V0 is the volume ofdischarge side 54A. The dimensions oftubes 66A-66C are selected such that the frequency of the discharge pulses of refrigerant R fromscrew rotors screw compressor 10 is configured to operate at 3,600 RPM at full load. Volume V0, therefore, comprises the volume ofdischarge side 54A whenpiston head 40 is furthest away from rod flange 50 (all the way to the left inFIG. 3 ), and frequency fR is 60 Hz. Thus, the areas and lengths oftubes 66A-66C are selected based on other design requirements, such as dimensional constraints ofrod flange 58 andslide case 16. Additionally, the number of tubes can be selected based on specific design considerations. In the embodiment shown,tubes 66A-66C have the same lengths and diameters. Thus, screwcompressor 10 is provided with a pulsation damper that is configured for damping pulsation effects of refrigerant R at a specific operating condition. However, in other embodiments,tubes 66A-66C can have different geometries, such as different lengths and/or different diameters, such that the pulsation damper is tuned to one specific resonance frequency, or can attenuate vibration and acoustic effects over a range of frequencies. In other embodiments of the invention,rod flange 58 comprises a circular disk or annular ring that can be bolted or otherwise secured topiston cylinder 54 withinslide case 16 such that pulsation dampers configured for different resonance frequencies can be interchangeably installed intoscrew compressor 10. - While the invention has been described with reference to an exemplary embodiment(s), it will be understood by those skilled in the art that various changes may be made and equivalents may be substituted for elements thereof without departing from the scope of the invention. In addition, many modifications may be made to adapt a particular situation or material to the teachings of the invention without departing from the essential scope thereof. Therefore, it is intended that the invention not be limited to the particular embodiment(s) disclosed, but that the invention will include all embodiments falling within the scope of the appended claims.
Claims (24)
1. An outlet case for a screw compressor comprising:
a main body portion having:
a first end configured for receiving discharged working matter from screw rotors in the compressor;
a second end configured for receiving a piston cylinder of a slide valve assembly; and
a rod flange dividing the first end from the second end; and
a pulsation damper carried by the main body to dampen pressure pulsations in the discharged working matter entering the piston cylinder.
2. The outlet case for a screw compressor of claim 1 wherein:
the first end is configured as a discharge pocket for receiving a slide valve of the slide valve assembly;
the rod flange includes an opening for receiving a piston rod of the slide valve assembly; and
the pulsation damper comprises a channel extending through the rod flange.
3. The outlet case of claim 2 wherein the second end of the main body portion is connected to a slide case having a piston cylinder for receiving a piston head of the slide valve assembly, the piston cylinder axially aligning with the rod flange and the discharge pocket.
4. The outlet case of claim 2 wherein the channel extends between the piston cylinder and the discharge pocket.
5. The outlet case of claim 4 wherein the channel permits working matter discharged from the screw rotors to pressurize the piston cylinder.
6. The outlet case of claim 5 wherein the pressurized working matter within the piston cylinder compresses to extract energy from working matter attempting to enter the piston cylinder.
7. The outlet case of claim 2 wherein the channel reduces an amplitude of a sound wave in the working matter as the working matter passes through the damping bore.
8. The outlet case of claim 1 wherein the pulsation damper comprises a plurality of channels extending into the internal cavity.
9. The outlet case of claim 8 wherein the plurality of channels have different geometries.
10. The outlet case of claim 9 and further comprising a plurality of tubes inserted into the plurality of damping bores.
11. A screw compressor comprising:
a housing for receiving a supply of working matter, the housing comprising:
a rotor case having a suction pocket and a slide recess;
an discharge case having a discharge pocket axially aligned with the slide recess; and
a slide case having a piston cylinder axially aligned with the discharge pocket;
a pair of intermeshing screw rotors disposed within the rotor case between the suction pocket and the slide recess for compressing the working matter and discharging the working matter into the discharge pocket;
a slide valve assembly disposed adjacent the pair of intermeshing screw rotors and axially_movable within the slide recess, discharge pocket and piston cylinder to regulate the capacity of the screw compressor; and
a pulsation damper carried by the discharge case to dampen pressure pulsations of working matter discharged from the screw rotors to the discharge pocket and passing into the piston cylinder.
12. The screw compressor of claim 11 wherein:
the slide valve assembly comprises:
a slide valve axially movable within the slide recess and the discharge pocket;
a piston head axially movable within the piston cylinder; and
a piston shaft connecting the slide valve with the piston head; and
the pulsation damper comprises:
a flange for separating the discharge pocket from the piston cylinder;
a bore for receiving the piston rod; and
a damping channel extending through the flange.
13. The screw compressor of claim 12 wherein the damping channel dampens vibration generated by the working matter.
14. The screw compressor of claim 12 wherein the pulsation damper comprises:
a resonance chamber enclosed within the piston cylinder between the piston head and the flange such that working matter pressurizes the resonance chamber.
15. The screw compressor of claim 14 wherein the damping channel reduces an amplitude of the working matter as the working matter enters the resonance chamber.
16. The screw compressor of claim 14 wherein the pulsation damper comprises a plurality of damping channels.
17. The screw compressor of claim 16 wherein the lengths and diameters of the damping tubes are selected to produce a Helmholtz resonator having a natural frequency matching a frequency of the discharged working matter.
18. The screw compressor of claim 16 and further comprising a plurality of damping tubes inserted through the plurality of damping channels.
19. The screw compressor of claim 11 wherein the pulsation damper further comprises a seal positioned between the bore and the flange.
20. A screw compressor comprising:
a housing for receiving a supply of working matter;
a pair of intermeshing screw rotors disposed within the housing for compressing and discharging the working matter in a series of discharge pulses;
a slide valve assembly movable within the housing to regulate the capacity of the screw compressor, the slide valve assembly comprising:
a slide valve axially movable between the pair of intermeshing screw rotors; and
a piston axially connected to the slide valve for actuating the position of the slide valve; and
a Helmholtz resonator axially positioned between the slide valve and the piston, and configured to extract energy from the discharged pulses of the working matter.
21. A method for reducing discharge pulsations in a screw compressor, the method comprising the steps of:
passing a working matter from a suction port of the screw compressor, through a set of screw rotors, and to a discharge port in the screw compressor to reduce a volume of the working matter;
positioning a slide valve along the screw rotors such that the slide valve extends into the discharge port;
connecting a piston assembly to the slide valve such that a piston rod extends from the discharge port, through a rod flange, and into a piston cylinder; and
positioning an inlet of a fluid compressing pulsation damper on the rod flange such that working matter entering the discharge port passes by the pulsation damper inlet to attenuate pulsations within the working matter as the working matter exits the set of screw rotors.
22. The method for reducing discharge pulsations of claim 21 and further comprising passing at least a portion of the working matter discharged from the set of screw rotors through the damping openings and into a resonance chamber positioned within the piston cylinder.
23. The method for reducing discharge pulsations of claim 21 and further comprising matching a natural frequency of the damping openings to a discharge frequency of the working matter from the set of screw rotors.
24. The screw compressor of claim 20 and further comprising:
a piston cylinder connected to the housing through a rod flange; and
a piston rod extending through the rod flange to connect the slide valve to the piston;
wherein the Helmholtz resonator is defined by the rod flange, the piston cylinder and the piston.
Applications Claiming Priority (1)
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PCT/US2007/021144 WO2009045187A1 (en) | 2007-10-01 | 2007-10-01 | Screw compressor pulsation damper |
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US20100209280A1 true US20100209280A1 (en) | 2010-08-19 |
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US12/678,401 Abandoned US20100209280A1 (en) | 2007-10-01 | 2007-10-01 | Screw compressor pulsation damper |
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US (1) | US20100209280A1 (en) |
EP (1) | EP2198125B1 (en) |
CN (1) | CN101809251B (en) |
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- 2007-10-01 ES ES07839131.5T patent/ES2629981T3/en active Active
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- 2007-10-01 WO PCT/US2007/021144 patent/WO2009045187A1/en active Application Filing
- 2007-10-01 EP EP07839131.5A patent/EP2198125B1/en not_active Revoked
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US20150144367A1 (en) * | 2012-04-24 | 2015-05-28 | C. & E. Fein Gmbh | Machine tool that can be guided manually and having a housing |
US10160111B2 (en) * | 2012-04-24 | 2018-12-25 | C. & E. Fein Gmbh | Machine tool that can be guided manually and having a housing |
US9518680B2 (en) | 2013-12-24 | 2016-12-13 | Dongbu Daewoo Electronics Corporation | Compressor and valve assembly thereof for reducing pulsation and/or noise |
US9903356B2 (en) | 2013-12-24 | 2018-02-27 | Dongbu Daewoo Electronics Corporation | Compressor and discharging muffler thereof |
US10808969B2 (en) | 2015-08-11 | 2020-10-20 | Carrier Corporation | Screw compressor economizer plenum for pulsation reduction |
US10830239B2 (en) | 2015-08-11 | 2020-11-10 | Carrier Corporation | Refrigeration compressor fittings |
US10941776B2 (en) | 2015-10-02 | 2021-03-09 | Carrier Corporation | Screw compressor resonator arrays |
US10180140B2 (en) | 2016-09-30 | 2019-01-15 | Ingersoll-Rand Company | Pulsation damper for compressors |
CN106382231A (en) * | 2016-11-04 | 2017-02-08 | 西安交通大学苏州研究院 | Active screw compressor gas pulsation attenuating device |
US10907870B2 (en) | 2016-11-15 | 2021-02-02 | Carrier Corporation | Muffler for lubricant separator |
US11808264B2 (en) | 2018-10-02 | 2023-11-07 | Carrier Corporation | Multi-stage resonator for compressor |
Also Published As
Publication number | Publication date |
---|---|
CN101809251A (en) | 2010-08-18 |
EP2198125A4 (en) | 2013-07-24 |
CN101809251B (en) | 2013-07-17 |
EP2198125B1 (en) | 2017-06-21 |
WO2009045187A1 (en) | 2009-04-09 |
ES2629981T3 (en) | 2017-08-17 |
EP2198125A1 (en) | 2010-06-23 |
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