EP1888982B1 - Methods and apparatus for reducing the noise level outputted by oil separator - Google Patents
Methods and apparatus for reducing the noise level outputted by oil separator Download PDFInfo
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- EP1888982B1 EP1888982B1 EP05755080A EP05755080A EP1888982B1 EP 1888982 B1 EP1888982 B1 EP 1888982B1 EP 05755080 A EP05755080 A EP 05755080A EP 05755080 A EP05755080 A EP 05755080A EP 1888982 B1 EP1888982 B1 EP 1888982B1
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- Prior art keywords
- oil separator
- muffling
- segment
- internal
- shell
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/12—Sound
Definitions
- This invention relates to oil separators for use in refrigeration and cooling systems, and, in particular, to methods and apparatus for reducing the noise levels outputted by an oil separator that is located within a refrigeration or cooling system.
- a water cooled chiller type refrigeration system 10 using a screw compressor 20 typically includes a condenser 30, a cooler 40, an oil separator 50, a condenser fan 60 and one or more expansion devices 70.
- the compressor 20 requires oil for lubrication, wherein the oil is typically entrained in a refrigerant.
- the combined oil and refrigerant mixture is carried through a compression cycle and discharged into the oil separator 50, where the oil must be removed from the refrigerant to allow for proper operation of the cooler 40. From the oil separator 50, the clean refrigerant flows to the condenser 30 and the separated oil is returned to the compressor 10.
- This excitement causes high vibration levels at the surface of the oil separator 50, and that, in turn, translates into high noise levels outputted by the oil separator. These excess noise levels can be distracting and bothersome, or, even worse, can be damaging to the hearing of those working around the oil separator 50 and/or can be in violation of applicable noise ordinances.
- US 5,784,784 discloses a refrigeration compressor muffler located in a refrigeration system externally of the compressor. Often, however, such equipment is subjected to high pressure differentials between the compressor discharge within the equipment and the atmosphere outside of the equipment. In such instances, the noise reduction equipment functions, in essence, as a pressure vessel, thus implicating strict design rules, certifications, and by consequence, added costs. Moreover, the added noise reduction equipment causes the refrigeration/cooling system to occupy a larger overall footprint, which is suboptimal and can even outweigh any beneficial noise reduction that actually is achieved through use of the equipment.
- US 4,730,695 discloses a muffler for use in a hermetically sealed compressor unit.
- an oil separator for use in a refrigeration or cooling system as claimed in claim 1.
- the muffling segment of the muffling apparatus is at least partially formed of an absorbing material.
- the absorbing material is effective to attenuate the energy of pressure waves/pulsations from the compressor into heat, thus reducing the resultant vibrations of (and, in turn, noise levels outputted from) the oil separator caused by energy from the waves/pulsations.
- the internal layer of the muffling segment of the muffling apparatus is made of the absorbing material, and the internal shell has a plurality of perforations/openings defined therein. Each opening provides a direct fluid/air pathway from the lumen to the internal layer of absorbing material. The purpose of the openings is to enable the pressure waves/pulsations that propagate through the lumen of the muffling segment to come into contact with the interval layer of absorbing material thus enabling the absorbing material to attenuate the pressure waves/pulsations.
- FIG. 1 is a schematic view of a known exemplary arrangement of a refrigeration/cooling system utilizing an oil separator.
- FIG. 2 is a perspective view of an exemplary embodiment of an oil separator muffling apparatus
- FIG. 3 is a side, cross-sectional view of the muffling apparatus of FIG. 2 taken along line 3-3 of FIG. 2 ;
- FIG. 4 is a perspective view, with partial cut away, of an exemplary oil separator wherein the muffling apparatus of FIGS. 2 and 3 has been placed within an internal area thereof.
- the present invention provides an oil separator comprising a muffling apparatus and method for reducing the noise level output by an oil separator of a refrigeration or cooling system, such as a water-cooled chiller type refrigeration system.
- the muffling apparatus is placed within the oil separator in order to attenuate pressure waves/pulsations that emanate from the compressor of the refrigeration system. As discussed above, such pressure waves/pulsations are believed to be responsible for creating vibrational forces that cause the oil separator surface to vibrate and, in turn, to disadvantageously generate high noise levels in its vicinity.
- Attenuation occurs during use of the mumping apparatus because the pressure waves/pulsations come into contact with an absorbing material located within a muffling segment of the muffling apparatus.
- the absorbing material attenuates the energy of the pressure waves/pulsations into heat and thus reduces the resultant vibrations of (and, in turn, noise level outputted from) the oil separator that are caused by energy from the pressure waves/pulsations.
- the muffling apparatus provides many benefits. In particular, not only does the muffling apparatus successfully reduce oil separator noise levels, but it does so while being sited within the oil separator, thus not requiring the refrigeration/cooling system to occupy added space and not exposing the muffling apparatus to high pressure differentials.
- the design of the muffling apparatus also provides costs savings, as will be discussed in detail below.
- FIGS. 2 and 3 depict an exemplary oil separator muffling apparatus 100.
- the muffling apparatus 100 has at least two segments, wherein each segment serves a different purpose in accordance with the present invention and is made of different materials or material combinations than the other segment(s).
- the segments are connected to each other as is known in the art, e.g., by welding, brazing and/or through the use of rivets.
- the muffling apparatus 100 has a first, muffling segment 1010 and a second, non-muffling segment 1020.
- the muffling segment 1010 has a tubular body comprised of an external shell 110 that surrounds an internal layer 120, wherein the internal layer has an internal shell 130 - that is, the external shell and the internal shell "sandwich" the internal layer.
- the number and arrangement of the shells 110, 130 and the internal layer 120 of the muffling segment 1010 to be as shown in FIGS. 2 and 3 , it is also within the scope of the present invention for the muffling segment to be comprised of more layers and/or more shells than are depicted in the Figures.
- the muffling segment 1010 has a first end 140, a second end 150 and a lumen 160 therebetween, wherein the lumen is surrounded by the internal shell 130.
- the second end 150 of the muffling segment 1010 is adapted for connection to a first end 1100 of the non-muffling segment 1020 by techniques known in the art, e.g., welding, brazing and/or through the use of rivets.
- the purpose of the muffling segment 1010 is to reduce the noise level output of the oil separator in which the muffling apparatus 100 is placed.
- at least the internal layer 120 of the muffling segment 1010 is made, at least partially, of a material that will absorb the energy from pressure waves (that emanate from the compressor and are transferred to the oil separator) and dissipate/attenuate that energy into absorbable heat.
- the external shell 110 and/or the internal shell 130 might also be made, at least partially, of such an absorbing material.
- the specific choice of the absorbing material can vary according to several factors, including but not limited to cost, dumping characteristics, availability and designer preference.
- the absorbing material is a fiberglass material.
- a currently preferred fiberglass material is comprised of glass fibers with a phenolic resin, wherein the material has a density in the range of about 86 kg/m 3 to about 105 kg/m 3 and a maximum temperature of about 177°C.
- the material(s) from which the external shell 110 and the internal shell 130 of the muffling segment 1010 are constructed should be strong and durable, yet inexpensive.
- the external shell 110 and the internal shell 130 can be constructed of different or identical materials; however, according to an exemplary embodiment of the present invention, both the external shell 110 and the internal shell 130 are constructed of a sheet metal material.
- a currently preferred sheet metal material is steel, but other metal-based materials can be utilized as well.
- the internal shell 130 of the muffling segment 1010 has a plurality of perforations or openings 170 defined therein.
- Each opening 170 provides direct fluid communication between the lumen 160 and the internal layer 120 of absorbing material.
- the purpose of the openings 170 is to enable the pressure waves/pulsations that are propagating/passing through the lumen 160 of the muffling segment 1010 to come into contact with the internal layer 120 of absorbing material, thus enabling the absorbing material to attenuate the pressure waves/pulsations.
- openings 170 can vary depending on several factors, including, but not limited to, the frequency of the pressure waves/pulsations that are expected to be encountered. According to a currently preferred embodiment of the present invention, openings 170 are defined in a range of about 10% to about 50% of the overall surface area of the internal shell 130. Moreover, although the openings 170 can have any shape and any spacing interval, it is currently preferred for the openings to be substantially round and spaced apart from each other at substantially identical distances, as best shown in FIG. 3 .
- the non-muffling segment 1020 of the muffling apparatus 100 also has a tubular body, and has first and second ends 1100, 1200.
- the first end 1100 of the non-muffling segment is connected to the second end 150 of the muffling segment 1010, and the second end 1200 of the muffling segment is connected to an internal area 510 of an oil separator 500, as shown in FIG. 4 .
- Such connections are made as is generally known in the art, e.g., via welding, brazing and/or through the use of rivets.
- the non-muffling segment 1020 of the muffling apparatus 100 can have more than one layer and can be made of more than one material, it is currently preferred to form the non-muffling segment of one layer and one material, wherein suitable materials include sheet metal materials such as steel.
- suitable materials include sheet metal materials such as steel.
- cost savings occurs because sheet metal material is less expensive to purchase as compared to the absorbing material used in the muffling segment 1010.
- design flexibility because one can purchase many different pre-formed shapes and sizes of the sheet metal material from which the non-muffling segment 1020 is formed.
- the size and shape of muffling apparatus 100 also can vary; however, the muffling apparatus 100 does have a non-straight overall shape.
- FIGS. 2 and 3 depict a muffling apparatus that has a curved shape.
- the non-straight shape of muffling apparatus 100 enables the apparatus to have a larger size (as compared to an apparatus with a straight shape) while still fitting within the space confines of the oil separator. That allows for a longer lumen 160 to be defined between the first and second ends 140, 150 of a the muffling segment 1010, thus providing added opportunities for pressure waves/pulsations to come into contact with the internal layer 120 via openings 170.
- muffling segment 1010 of muffling apparatus 100 has a substantially straight shape and non-muffling segment 1020 has a curved shape.
- Such an arrangement is advantageous because a cost savings is achieved by not forming the muffling apparatus entirely of the muffling segment materials, yet the muffling apparatus is still capable of providing significant noise reduction, as will be discussed in more detail below.
- support element 600 is attached (e.g., by welding) to the first end 150 of the muffling segment 1010 and to the internal area 510 of the oil separator 500.
- the presence of the support element 600 provides added support to muffling apparatus 100 by bearing the weight of muffling segment 1010.
- Support element 600 can be made of a variety of materials, including, but not limited, to one or more metal-based materials (e.g., steel).
- the size of the muffling apparatus 100 can vary depending on several factors, most notably the size of the oil separator in which the ruffling apparatus is installed. It is currently preferred for the size of the muffling apparatus 100 to vary proportionally with the size of the oil separator.
- the muffling apparatus 100 will have a different predetermined size in order to fit within a 14 inch (35.6 cm) oil separator than it would to fit within a 16 inch (40.6 cm) oil separator or an 18 inch (45.7 cm) oil separator, wherein the size of the muffling apparatus for a 16 inch (40.6 cm) oil separator generally will be approximately 16/14 times the size of the muffling apparatus for a 14 inch (35.6 cm) oil separator and approximately 16/18 times the size of the muffling apparatus for an 18 inch (45.7 cm) oil separator.
- the effective height, H (see FIG. 3 ), occupied by the muffling apparatus is in the range of about 7.5 inches to about 9.5 inches (19.1 to 24.1 cm), with an effective height of about 8.5 inches (21.6 cm) being currently preferred, and the effective length, L (see FIG. 3 ) occupied by the muffling apparatus is in the range of about 11 inches to about 13.5 inches (27.9 to 34.3 cm) with an effective height of about 13.2 inches (33.5 cm) being currently preferred.
- the length of muffling segment 1010 also can vary according to several factors, including the frequency of the pressure waves expected to the encountered within the oil separator. For example, the length of muffling segment 1010 can be comparatively greater when the frequency of the pressure waves is expected to be about 2000Hz versus 125Hz. According to an exemplary embodiment of the present invention in which muffling apparatus 100 is placed within a 14 inch (35.6 cm) oil separator, the length of the muffling segment 1010 is about 4.5 inches to about 6.5 inches (11.4 to 16.5 cm) wherein a length of about 6 inches (15.2 cm) currently preferred. Stated differently, the length of muffling segment 1010 generally comprises about 30% to about 60% of the overall length, L, of the muffling apparatus 100. For placement within a 16 inch (40.6 cm) and 18 inch (45.7cm) oil separators, the length measurements would be approximately 16/14 times greater and 18/14 times greater, respectively.
- a refrigeration system was first operated such that its oil separator encountered six different pressure wave frequencies (125 Hz, 250 Hz, 500 Hz, 1000 Hz, 2000 Hz and 4000Hz) emanating from its compressor, wherein the noise level outputted by the oil separator in response to each of these pressure wave levels was measured and recorded.
- a muffling apparatus 100 of the type shown in FIGS. 2 and 3 was then installed within the oil separator and the testing conditions were repeated to gather comparable data.
- the experimental results in Table I demonstrate that there was an acoustic reduction at each pressure wave frequency level due to the presence of the muffling apparatus 100, wherein the acoustic reduction was calculated as the difference between the acoustic level at the oil separator without a muffling apparatus versus the acoustic level at the same oil separator with a muffling apparatus of the present invention installed within an internal area thereof. Therefore, the -12 dB measurement at 250 Hz indicates that the noise level measurement taken after the muffling apparatus 100 was installed within the oil separator was 12 dB less than the measurement taken when the same oil separator was not equipped with the muffling apparatus.
- the Global dBA of -4 dBA also supports that there was an acoustic reduction, and that the dominant frequency band of the pressure weves/pulsations was in the range of about 500-1000Hz.
- a muffling apparatus 100 of the type shown in FIGS. 2 and 3 can be installed in an oil separator with confidence that the noise level reduction will be at least 1dB, with a noise reduction level of up to 12 dB being possible as well depending on the dominant frequency band of the pressure/wave pulsations emanating from the compressor.
- noise reduction levels especially when considering the effects of exposure to the reduced noise level over the lifetime of the refrigeration system in which the oil separator is located.
- a noise reduction level of between 1dH and 12dB will be even more significant if, as is commonly the case, multiple refrigeration systems that include oil separators are installed in close proximity.
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Abstract
Description
- This invention relates to oil separators for use in refrigeration and cooling systems, and, in particular, to methods and apparatus for reducing the noise levels outputted by an oil separator that is located within a refrigeration or cooling system.
- As illustrated by
FIG. 1 , a water cooled chillertype refrigeration system 10 using ascrew compressor 20 typically includes acondenser 30, acooler 40, anoil separator 50, acondenser fan 60 and one ormore expansion devices 70. Thecompressor 20 requires oil for lubrication, wherein the oil is typically entrained in a refrigerant. The combined oil and refrigerant mixture is carried through a compression cycle and discharged into theoil separator 50, where the oil must be removed from the refrigerant to allow for proper operation of thecooler 40. From theoil separator 50, the clean refrigerant flows to thecondenser 30 and the separated oil is returned to thecompressor 10. - Most known oil separators, such as those described in
U.S. Patent No. 5,704,215 to Lord et al. , perform this separation function well.WO 98/15789 oil separator 50 within a refrigeration system, such as thesystem 100 illustrated inFIG. 1 . Without wishing to be bound by theory, it is believed that this is caused by high level pressure waves/pulsations (i.e., 250 Hz or above) emanating from thecompressor 20 that are transferred to theoil separator 50, which acts like a resonant cavity and thus is excited by the compressor pulsations. This excitement causes high vibration levels at the surface of theoil separator 50, and that, in turn, translates into high noise levels outputted by the oil separator. These excess noise levels can be distracting and bothersome, or, even worse, can be damaging to the hearing of those working around theoil separator 50 and/or can be in violation of applicable noise ordinances. - Previous efforts by those in the art to reduce the high noise levels produced by an
oil separator 50 have focused on placing noise reduction equipment or devices between the oil separator and thecompressor 20. For example,US 5,784,784 discloses a refrigeration compressor muffler located in a refrigeration system externally of the compressor. Often, however, such equipment is subjected to high pressure differentials between the compressor discharge within the equipment and the atmosphere outside of the equipment. In such instances, the noise reduction equipment functions, in essence, as a pressure vessel, thus implicating strict design rules, certifications, and by consequence, added costs. Moreover, the added noise reduction equipment causes the refrigeration/cooling system to occupy a larger overall footprint, which is suboptimal and can even outweigh any beneficial noise reduction that actually is achieved through use of the equipment.
US 4,730,695 discloses a muffler for use in a hermetically sealed compressor unit. - Therefore, a need exists for methods and apparatus to reduce the noise output of an oil separator without interfering with the functioning of the oil separator or any other equipment utilized in connection with the refrigeration system, and wherein such methods and apparatus would not be plagued by any of the various drawbacks associated with muffling apparatus known in the art.
- These and other needs are met by the present invention.
According to an aspect of the present invention there is provided an oil separator for use in a refrigeration or cooling system as claimed in claim 1.
According to another aspect of the present invention there is provided a method for reducing the noise level outputted by an oil separator within a refrigeration or cooling system as claimed in claim 6. - The muffling segment of the muffling apparatus is at least partially formed of an absorbing material. The absorbing material is effective to attenuate the energy of pressure waves/pulsations from the compressor into heat, thus reducing the resultant vibrations of (and, in turn, noise levels outputted from) the oil separator caused by energy from the waves/pulsations.
- The internal layer of the muffling segment of the muffling apparatus is made of the absorbing material, and the internal shell has a plurality of perforations/openings defined therein. Each opening provides a direct fluid/air pathway from the lumen to the internal layer of absorbing material. The purpose of the openings is to enable the pressure waves/pulsations that propagate through the lumen of the muffling segment to come into contact with the interval layer of absorbing material thus enabling the absorbing material to attenuate the pressure waves/pulsations.
- Still other aspects, embodiments and advantages of the present invention are discussed in detail below.
- For a fuller understanding of the nature and desired objects of the present invention, reference is made to the following detailed description taken in conjunction with the accompanying figures, wherein like reference characters denote corresponding parts throughout the views, and in which:
-
FIG. 1 is a schematic view of a known exemplary arrangement of a refrigeration/cooling system utilizing an oil separator. -
FIG. 2 is a perspective view of an exemplary embodiment of an oil separator muffling apparatus; -
FIG. 3 is a side, cross-sectional view of the muffling apparatus ofFIG. 2 taken along line 3-3 ofFIG. 2 ; and -
FIG. 4 is a perspective view, with partial cut away, of an exemplary oil separator wherein the muffling apparatus ofFIGS. 2 and3 has been placed within an internal area thereof. - The present invention provides an oil separator comprising a muffling apparatus and method for reducing the noise level output by an oil separator of a refrigeration or cooling system, such as a water-cooled chiller type refrigeration system. The muffling apparatus is placed within the oil separator in order to attenuate pressure waves/pulsations that emanate from the compressor of the refrigeration system. As discussed above, such pressure waves/pulsations are believed to be responsible for creating vibrational forces that cause the oil separator surface to vibrate and, in turn, to disadvantageously generate high noise levels in its vicinity.
- Attenuation occurs during use of the mumping apparatus because the pressure waves/pulsations come into contact with an absorbing material located within a muffling segment of the muffling apparatus. The absorbing material attenuates the energy of the pressure waves/pulsations into heat and thus reduces the resultant vibrations of (and, in turn, noise level outputted from) the oil separator that are caused by energy from the pressure waves/pulsations.
- The muffling apparatus provides many benefits. In particular, not only does the muffling apparatus successfully reduce oil separator noise levels, but it does so while being sited within the oil separator, thus not requiring the refrigeration/cooling system to occupy added space and not exposing the muffling apparatus to high pressure differentials. The design of the muffling apparatus also provides costs savings, as will be discussed in detail below.
-
FIGS. 2 and3 depict an exemplary oilseparator muffling apparatus 100. Themuffling apparatus 100 has at least two segments, wherein each segment serves a different purpose in accordance with the present invention and is made of different materials or material combinations than the other segment(s). The segments are connected to each other as is known in the art, e.g., by welding, brazing and/or through the use of rivets. - As is currently preferred, and as is best shown in
FIG. 3 , themuffling apparatus 100 has a first, mufflingsegment 1010 and a second,non-muffling segment 1020. Themuffling segment 1010 has a tubular body comprised of anexternal shell 110 that surrounds aninternal layer 120, wherein the internal layer has an internal shell 130 - that is, the external shell and the internal shell "sandwich" the internal layer. Although it is currently preferred for the number and arrangement of theshells internal layer 120 of themuffling segment 1010 to be as shown inFIGS. 2 and3 , it is also within the scope of the present invention for the muffling segment to be comprised of more layers and/or more shells than are depicted in the Figures. - The
muffling segment 1010 has afirst end 140, asecond end 150 and alumen 160 therebetween, wherein the lumen is surrounded by theinternal shell 130. Thesecond end 150 of themuffling segment 1010 is adapted for connection to afirst end 1100 of thenon-muffling segment 1020 by techniques known in the art, e.g., welding, brazing and/or through the use of rivets. - As noted above, the purpose of the
muffling segment 1010 is to reduce the noise level output of the oil separator in which themuffling apparatus 100 is placed. To enable that to occur; at least theinternal layer 120 of themuffling segment 1010 is made, at least partially, of a material that will absorb the energy from pressure waves (that emanate from the compressor and are transferred to the oil separator) and dissipate/attenuate that energy into absorbable heat. It is also contemplated, however, that theexternal shell 110 and/or theinternal shell 130 might also be made, at least partially, of such an absorbing material. The specific choice of the absorbing material can vary according to several factors, including but not limited to cost, dumping characteristics, availability and designer preference. According to an exemplary embodiment of the present invention, the absorbing material is a fiberglass material. A currently preferred fiberglass material is comprised of glass fibers with a phenolic resin, wherein the material has a density in the range of about 86 kg/m3 to about 105 kg/m3 and a maximum temperature of about 177°C. - The material(s) from which the
external shell 110 and theinternal shell 130 of themuffling segment 1010 are constructed should be strong and durable, yet inexpensive. Theexternal shell 110 and theinternal shell 130 can be constructed of different or identical materials; however, according to an exemplary embodiment of the present invention, both theexternal shell 110 and theinternal shell 130 are constructed of a sheet metal material. A currently preferred sheet metal material is steel, but other metal-based materials can be utilized as well. - As shown in
FIGS. 2 and3 , theinternal shell 130 of themuffling segment 1010 has a plurality of perforations oropenings 170 defined therein. Eachopening 170 provides direct fluid communication between thelumen 160 and theinternal layer 120 of absorbing material. The purpose of theopenings 170 is to enable the pressure waves/pulsations that are propagating/passing through thelumen 160 of themuffling segment 1010 to come into contact with theinternal layer 120 of absorbing material, thus enabling the absorbing material to attenuate the pressure waves/pulsations. - The size, shape, number and spacing interval of the
openings 170 can vary depending on several factors, including, but not limited to, the frequency of the pressure waves/pulsations that are expected to be encountered. According to a currently preferred embodiment of the present invention,openings 170 are defined in a range of about 10% to about 50% of the overall surface area of theinternal shell 130. Moreover, although theopenings 170 can have any shape and any spacing interval, it is currently preferred for the openings to be substantially round and spaced apart from each other at substantially identical distances, as best shown inFIG. 3 . - The
non-muffling segment 1020 of themuffling apparatus 100 also has a tubular body, and has first andsecond ends first end 1100 of the non-muffling segment is connected to thesecond end 150 of themuffling segment 1010, and thesecond end 1200 of the muffling segment is connected to aninternal area 510 of anoil separator 500, as shown inFIG. 4 . Such connections are made as is generally known in the art, e.g., via welding, brazing and/or through the use of rivets. - Although the
non-muffling segment 1020 of themuffling apparatus 100 can have more than one layer and can be made of more than one material, it is currently preferred to form the non-muffling segment of one layer and one material, wherein suitable materials include sheet metal materials such as steel. There are several advantages of forming thenon-muffling segment 1020 of the muffling apparatus entirely from a metal-based material, including, but not limited to, cost savings and design flexibility. The cost savings occurs because sheet metal material is less expensive to purchase as compared to the absorbing material used in themuffling segment 1010. Also, there is design flexibility because one can purchase many different pre-formed shapes and sizes of the sheet metal material from which thenon-muffling segment 1020 is formed. - The size and shape of muffling
apparatus 100 also can vary; however, themuffling apparatus 100 does have a non-straight overall shape. For example,FIGS. 2 and3 depict a muffling apparatus that has a curved shape. The non-straight shape of mufflingapparatus 100 enables the apparatus to have a larger size (as compared to an apparatus with a straight shape) while still fitting within the space confines of the oil separator. That allows for alonger lumen 160 to be defined between the first and second ends 140, 150 of a themuffling segment 1010, thus providing added opportunities for pressure waves/pulsations to come into contact with theinternal layer 120 viaopenings 170. - As shown in
FIGS. 2 and3 , mufflingsegment 1010 of mufflingapparatus 100 has a substantially straight shape andnon-muffling segment 1020 has a curved shape. Such an arrangement is advantageous because a cost savings is achieved by not forming the muffling apparatus entirely of the muffling segment materials, yet the muffling apparatus is still capable of providing significant noise reduction, as will be discussed in more detail below. - Optionally, and as shown in the Figures,
support element 600 is attached (e.g., by welding) to thefirst end 150 of themuffling segment 1010 and to theinternal area 510 of theoil separator 500. The presence of thesupport element 600 provides added support to mufflingapparatus 100 by bearing the weight ofmuffling segment 1010.Support element 600 can be made of a variety of materials, including, but not limited, to one or more metal-based materials (e.g., steel). - The size of the
muffling apparatus 100 can vary depending on several factors, most notably the size of the oil separator in which the ruffling apparatus is installed. It is currently preferred for the size of themuffling apparatus 100 to vary proportionally with the size of the oil separator. For example, themuffling apparatus 100 will have a different predetermined size in order to fit within a 14 inch (35.6 cm) oil separator than it would to fit within a 16 inch (40.6 cm) oil separator or an 18 inch (45.7 cm) oil separator, wherein the size of the muffling apparatus for a 16 inch (40.6 cm) oil separator generally will be approximately 16/14 times the size of the muffling apparatus for a 14 inch (35.6 cm) oil separator and approximately 16/18 times the size of the muffling apparatus for an 18 inch (45.7 cm) oil separator. - According to an exemplary embodiment of the present invention in which the
muffling apparatus 100 is placed in a 14 inch (35.6 cm) oil separator, the effective height, H (seeFIG. 3 ), occupied by the muffling apparatus is in the range of about 7.5 inches to about 9.5 inches (19.1 to 24.1 cm), with an effective height of about 8.5 inches (21.6 cm) being currently preferred, and the effective length, L (seeFIG. 3 ) occupied by the muffling apparatus is in the range of about 11 inches to about 13.5 inches (27.9 to 34.3 cm) with an effective height of about 13.2 inches (33.5 cm) being currently preferred. For placement within a 16 inch (40.6 cm) oil separator, these measurements would be approximately 16/14 times those for the 14 inch (35.6 cm) oil separator, and for placement within an 18 inch (45.7 cm) oil separator, they would be approximately 18/14 times those for the 14 inch (35.6 cm) oil separator. - The length of
muffling segment 1010 also can vary according to several factors, including the frequency of the pressure waves expected to the encountered within the oil separator. For example, the length ofmuffling segment 1010 can be comparatively greater when the frequency of the pressure waves is expected to be about 2000Hz versus 125Hz. According to an exemplary embodiment of the present invention in whichmuffling apparatus 100 is placed within a 14 inch (35.6 cm) oil separator, the length of themuffling segment 1010 is about 4.5 inches to about 6.5 inches (11.4 to 16.5 cm) wherein a length of about 6 inches (15.2 cm) currently preferred. Stated differently, the length ofmuffling segment 1010 generally comprises about 30% to about 60% of the overall length, L, of themuffling apparatus 100. For placement within a 16 inch (40.6 cm) and 18 inch (45.7cm) oil separators, the length measurements would be approximately 16/14 times greater and 18/14 times greater, respectively. - Experiments were conducted to assess the noise reduction efficacy of the
muffling apparatus 100. The experiments were performed in accordance with the guidelines of International Organization for Standardization (ISO 9614). The results of the experiments are shown in Table I below;Table I Pressure Wave (octave in Hz) 125 250 500 1000 2000 4000 Acoustic change (dB) due to presence of muffling apparatus -1 -12 -6 -1 -7 -12 Global dBA = -4 - To accumulate the test results in Table I, a refrigeration system was first operated such that its oil separator encountered six different pressure wave frequencies (125 Hz, 250 Hz, 500 Hz, 1000 Hz, 2000 Hz and 4000Hz) emanating from its compressor, wherein the noise level outputted by the oil separator in response to each of these pressure wave levels was measured and recorded. A
muffling apparatus 100 of the type shown inFIGS. 2 and3 was then installed within the oil separator and the testing conditions were repeated to gather comparable data. - The experimental results in Table I demonstrate that there was an acoustic reduction at each pressure wave frequency level due to the presence of the
muffling apparatus 100, wherein the acoustic reduction was calculated as the difference between the acoustic level at the oil separator without a muffling apparatus versus the acoustic level at the same oil separator with a muffling apparatus of the present invention installed within an internal area thereof. Therefore, the -12 dB measurement at 250 Hz indicates that the noise level measurement taken after themuffling apparatus 100 was installed within the oil separator was 12 dB less than the measurement taken when the same oil separator was not equipped with the muffling apparatus. The Global dBA of -4 dBA also supports that there was an acoustic reduction, and that the dominant frequency band of the pressure weves/pulsations was in the range of about 500-1000Hz. - The results in Table I are very favorable. In particular, noise reduction levels were observed for each of the six selected pressure wave frequency bands. This is important because different compressors operate at different dominant pressure output levels, and thus would produce different Global dBA measurements. Moreover, noise reduction occurred despite the fact that the muffling apparatus was only partially formed of a
muffling segment 1010. This signifies that by forming the muffling apparatus from amuffling segment 1010 and anon-muffling segment 1020, one can achieve noise reduction while enjoying cost savings and design flexibility. - Thus, a
muffling apparatus 100 of the type shown inFIGS. 2 and3 can be installed in an oil separator with confidence that the noise level reduction will be at least 1dB, with a noise reduction level of up to 12 dB being possible as well depending on the dominant frequency band of the pressure/wave pulsations emanating from the compressor. These are significant noise reduction levels, especially when considering the effects of exposure to the reduced noise level over the lifetime of the refrigeration system in which the oil separator is located. Moreover, a noise reduction level of between 1dH and 12dB will be even more significant if, as is commonly the case, multiple refrigeration systems that include oil separators are installed in close proximity.
Claims (9)
- An oil separator (500) for use in a refrigeration or cooling system comprising a muffling apparatus (100) for reducing the noise level output by the oil separator, the muffling apparatus being placed within an internal area of the oil separator, and wherein the muffling apparatus (100) comprises:a first muffling segment (1010) having a straight tubular body with a first end (140), a second end (150) and a lumen (160) therebetween, wherein the first segment is comprised of:an external shell (110);an internal layer (120) formed at least partially of an absorbing material, wherein the internal layer (120) is surrounded by the external shell (110); andan internal shell (130), wherein the internal shell surrounds the lumen, and wherein the internal shell (130) has a plurality of openings (170) defined therein to enable direct fluid communication between the absorbing material and the lumen (160); anda second non-muffling segment (1020) having a curved or bent tubular body with a first end (1100) and a second end (1200);wherein the first end (1100) of the second segment (1020) is connected to the second end (150) of the first segment (1010), and the second end (1200) of the second segment (1020) is attached to the internal area (510) of the oil separator (500).
- The oil separator of claim 1, wherein the absorbing material is a fibreglass material.
- The oil separator of claim 1 or 2, wherein each of the external shell (110) and the internal shell (130) is made of a sheet metal material.
- The oil separator of any preceding claim, wherein the muffling apparatus (100) is attached to a first end of a support element (600), and wherein a second end of the support element (600) is attached to the internal area of the oil separator (500).
- A refrigeration or cooling system comprising:a compressor; andan oil separator (500) as claimed in any preceding claim for separating oil from the combined oil and refrigerant mixture discharged from the compressor;wherein the muffling apparatus (100) within the oil separator (500) is arranged to attenuate pressure waves that emanate from the compressor.
- A method for reducing the noise level outputted by an oil separator within a refrigeration or cooling system, comprising:providing a muffling apparatus (100); andplacing the muffling apparatus (100) within an internal area of an oil separator (500) by attaching the muffling apparatus to the internal area of the oil separator;wherein the muffling apparatus (100) comprises:a first muffling segment (1010) having a straight tubular body with a first end (140), a second end (150) and a lumen (160) therebetween, wherein the first segment is comprised of:an external shell (110);an internal layer (120) formed at least partially of an absorbing material, wherein the internal layer (120) is surrounded by the external shell (110); andan internal shell (130), wherein the internal shell surrounds the lumen, and wherein the internal shell (130) has a plurality of openings (170) defined therein to enable direct fluid communication between the absorbing material and the lumen (160): anda second non-muffling segment (1020) having a curved or bent tubular body with a first end (1100) and a second end (1200); andwherein the first end (1100) of the second segment (1020) is connected to the second end (150) of the first segment (1010), and the second end (1200) of the second segment (1020) is attached to the internal area (510) of the oil separator (500).
- The method of claim 6, wherein the absorbing material is a fibreglass material.
- The method of claim 6 or 7, wherein each of the external shell (110) and the internal shell (130) is made of a sheet metal material.
- The method of any of claims 6 to 8. wherein the muffling apparatus (100) is attached to a first end of a support element (600), and wherein a second end of the support element (600) is attached to the internal area of the oil separator (500).
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/US2005/018827 WO2006130131A1 (en) | 2005-05-31 | 2005-05-31 | Methods and apparatus for reducing the noise level outputted by oil separator |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1888982A1 EP1888982A1 (en) | 2008-02-20 |
EP1888982B1 true EP1888982B1 (en) | 2010-12-15 |
Family
ID=35448165
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP05755080A Not-in-force EP1888982B1 (en) | 2005-05-31 | 2005-05-31 | Methods and apparatus for reducing the noise level outputted by oil separator |
Country Status (9)
Country | Link |
---|---|
US (1) | US20080179134A1 (en) |
EP (1) | EP1888982B1 (en) |
CN (1) | CN101228402B (en) |
AT (1) | ATE491920T1 (en) |
BR (1) | BRPI0520251A2 (en) |
DE (1) | DE602005025418D1 (en) |
ES (1) | ES2355919T3 (en) |
HK (1) | HK1123090A1 (en) |
WO (1) | WO2006130131A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11536501B2 (en) | 2018-09-14 | 2022-12-27 | Carrier Corporation | Oil separator with integrated muffler |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8276398B2 (en) * | 2005-05-31 | 2012-10-02 | Carrier Corporation | Methods and apparatus for reducing the noise level outputted by oil separator |
US10907870B2 (en) | 2016-11-15 | 2021-02-02 | Carrier Corporation | Muffler for lubricant separator |
CN109386505B (en) | 2017-08-09 | 2022-02-11 | 开利公司 | Silencer for refrigerating device and refrigerating device |
DE102018108559A1 (en) * | 2018-04-11 | 2019-10-17 | Alfred Kärcher SE & Co. KG | cleaner |
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US2809813A (en) * | 1955-01-24 | 1957-10-15 | Wendell S Fletcher | Muffling and oil-cooling device |
US5007499A (en) * | 1990-02-23 | 1991-04-16 | Carrier Corporation | Silencer for a centrifugal compressor |
DE19522383A1 (en) * | 1995-06-23 | 1997-01-02 | Danfoss Compressors Gmbh | Suction silencer for a refrigerant compressor |
US5784784A (en) * | 1995-10-20 | 1998-07-28 | Carrier Corporation | Method of making a refrigeration compressor muffler |
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JPS5933898Y2 (en) * | 1980-01-16 | 1984-09-20 | 日産自動車株式会社 | Silencer |
IT1191513B (en) * | 1986-01-10 | 1988-03-23 | Necchi Spa | SILENCER FOR HERMETIC COMPRESSOR |
CN87211863U (en) * | 1987-08-12 | 1988-09-28 | 沈世莹 | Low-resistance and corrosion resistant damper bend |
US5101930A (en) * | 1990-08-28 | 1992-04-07 | Otis Elevator Company | Hydraulic elevator muffler |
US5214937A (en) * | 1991-10-28 | 1993-06-01 | Carrier Corporation | Integral oil separator and muffler |
US5326942A (en) * | 1993-02-09 | 1994-07-05 | Schmid Jerry W | Noise suppression muffler for moisture laden exhaust gases & method |
JPH0868490A (en) * | 1994-08-26 | 1996-03-12 | Excel Kk | Hollow molding body with muffler part |
JPH08159619A (en) * | 1994-12-02 | 1996-06-21 | Mitsubishi Heavy Ind Ltd | Oil separator and air compressor equipped with the separator |
CN2230816Y (en) * | 1995-02-25 | 1996-07-10 | 简忠民 | Exhaust and inlet air purifier |
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DE19907264C1 (en) * | 1999-02-20 | 2000-10-05 | Webasto Thermosysteme Gmbh | Air intake silencer with water separator |
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US7537084B2 (en) * | 2004-09-03 | 2009-05-26 | York International Corporation | Discharge gas check valve integral with muffler |
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2005
- 2005-05-31 ES ES05755080T patent/ES2355919T3/en active Active
- 2005-05-31 DE DE602005025418T patent/DE602005025418D1/en active Active
- 2005-05-31 EP EP05755080A patent/EP1888982B1/en not_active Not-in-force
- 2005-05-31 BR BRPI0520251-5A patent/BRPI0520251A2/en not_active IP Right Cessation
- 2005-05-31 AT AT05755080T patent/ATE491920T1/en not_active IP Right Cessation
- 2005-05-31 CN CN2005800512259A patent/CN101228402B/en not_active Expired - Fee Related
- 2005-05-31 WO PCT/US2005/018827 patent/WO2006130131A1/en active Search and Examination
-
2006
- 2006-12-07 US US11/915,799 patent/US20080179134A1/en not_active Abandoned
-
2009
- 2009-01-13 HK HK09100334.6A patent/HK1123090A1/en not_active IP Right Cessation
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US2809813A (en) * | 1955-01-24 | 1957-10-15 | Wendell S Fletcher | Muffling and oil-cooling device |
US5007499A (en) * | 1990-02-23 | 1991-04-16 | Carrier Corporation | Silencer for a centrifugal compressor |
DE19522383A1 (en) * | 1995-06-23 | 1997-01-02 | Danfoss Compressors Gmbh | Suction silencer for a refrigerant compressor |
US5784784A (en) * | 1995-10-20 | 1998-07-28 | Carrier Corporation | Method of making a refrigeration compressor muffler |
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US11536501B2 (en) | 2018-09-14 | 2022-12-27 | Carrier Corporation | Oil separator with integrated muffler |
Also Published As
Publication number | Publication date |
---|---|
ATE491920T1 (en) | 2011-01-15 |
CN101228402A (en) | 2008-07-23 |
BRPI0520251A2 (en) | 2009-09-15 |
WO2006130131A1 (en) | 2006-12-07 |
DE602005025418D1 (en) | 2011-01-27 |
ES2355919T3 (en) | 2011-04-01 |
US20080179134A1 (en) | 2008-07-31 |
CN101228402B (en) | 2012-04-18 |
EP1888982A1 (en) | 2008-02-20 |
HK1123090A1 (en) | 2009-06-05 |
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