SCREW COMPRESSOR PULSATION DAMPER
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).
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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.
SUMMARYExemplary 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.
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 50A-50D. For example, slide valve 36 can be extended to the fully-loaded position (to the left in
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 56A, which is exposed to refrigerant R at pressure P2, and second pressure side 56B, which is exposed to control oil at pressure P3. Pressure P2 is dictated by refrigerant R and screw rotors 18 and 20, while pressure P3 is regulated by 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 P3 to exert a force on second pressure side 56B to move slide valve 36 toward slide stop 52 within slide recess 51. Pressure P3 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 56A to assist in withdrawing slide valve 36 from slide recess 51. Piston head 40 is also in contact with refrigerant R, which exerts pressure P2 on first pressure side 56A to push piston head 40 away from rod flange 58. Refrigerant R, is admitted into piston cylinder 54 through damping channels 46A and 46B disposed within rod flange 58. Damping channels 46A and 46B, 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. Specifically, damping channels 46A and 46B act in concert with piston cylinder 54 to provide a Helmholtz resonator to absorb energy from the discharged pulses of refrigerant R.
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). In the embodiment shown, 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 64A and 64B, which are disposed within grooves in ring 62. In one embodiment, 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. In another embodiment, 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 46A-46C, 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 54A and control side 54B. 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 54A of this sealed canister, however, also acts as a resonance chamber, that along with damping channels 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 (
In the embodiment shown in
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 54A, refrigerant R and channels 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 fills discharge side 54A such that additional refrigerant attempting to enter discharge side 54A through channels 46A-46C must compress the volume of refrigerant R already present within discharge side 54A. Thus, a pulsed wave of refrigerant R attempting to enter discharge side 54A, compresses refrigerant R until the crest of the wave is reached. Then, the pressurized refrigerant R within discharge 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 within discharge side 54A 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. Thus, the resonance frequency of the Helmholtz resonator produced by discharge side 54A and damping channels 46A-46C 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 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 in
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
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.
Type: Application
Filed: Oct 1, 2007
Publication Date: Aug 19, 2010
Applicant: CARRIER CORPORATION (Farmington, CT)
Inventors: Paul J. Flannigan (Cicero, NY), Bruce A. Fraser (Manlius, NY)
Application Number: 12/678,401
International Classification: F04C 18/16 (20060101);