Source: https://patents.google.com/patent/US9458845B2/en
Timestamp: 2018-08-21 03:28:30
Document Index: 509900648

Matched Legal Cases: ['§120', 'application No. 61', '§120', 'application No. 61', '§120', 'application No. 61', '§120', 'application No. 61', '§120', 'application No. 61']

US9458845B2 - Air ducting shroud for cooling an air compressor pump and motor - Google Patents
Air ducting shroud for cooling an air compressor pump and motor Download PDF
US9458845B2
US9458845B2 US13609331 US201213609331A US9458845B2 US 9458845 B2 US9458845 B2 US 9458845B2 US 13609331 US13609331 US 13609331 US 201213609331 A US201213609331 A US 201213609331A US 9458845 B2 US9458845 B2 US 9458845B2
US13609331
US20130064641A1 (en )
A compressor assembly having an air ducting shroud that can direct a cooling air stream from a fan to components of the compressor assembly, such as a pump assembly. The pump assembly can have at least a pump, a motor and a fan. The compressor can be cooled by providing cooling air to a cylinder head of the pump without the cooling air experiencing choking or substantial cooling flow interference from a cooling of the motor.
This patent application claims benefit of the filing date under 35 USC §120 of U.S. provisional patent application No. 61/533,993 entitled “Air Ducting Shroud For Cooling An Air Compressor Pump And Motor” filed on Sep. 13, 2011. This patent application claims benefit of the filing date under 35 USC §120 of U.S. provisional patent application No. 61/534,001 entitled “Shroud For Capturing Fan Noise” filed on Sep. 13, 2011. This patent application claims benefit of the filing date under 35 USC §120 of U.S. provisional patent application No. 61/534,009 entitled “Method Of Reducing Air Compressor Noise” filed on Sep. 13, 2011. This patent application claims benefit of the filing date under 35 USC §120 of U.S. provisional patent application No. 61/534,015 entitled “Tank Dampening Device” filed on Sep. 13, 2011. This patent application claims benefit of the filing date under 35 USC §120 of U.S. provisional patent application No. 61/534,046 entitled “Compressor Intake Muffler And Filter” filed on Sep. 13, 2011.
In an embodiment, the compressor assembly disclosed herein can have a fan; a pump assembly; an air ducting shroud which directs cooling air to a member of the pump assembly and which is adapted to dampen a noise from the pump assembly; and a sound level having a value of 75 dBA or less when the compressor is in a compressing state.
The compressor assembly can have an air ducting shroud which encases at least a portion of the fan. The compressor assembly can have an air ducting shroud which encases at least a portion of a motor of the pump assembly. The compressor assembly can have an air ducting shroud which has a conduit which directs a cooling air flow to a cylinder head of the pump assembly. The compressor assembly can have an air ducting shroud which directs a cooling air flow to at least a portion of a motor of the pump assembly. The compressor assembly can have an air ducting shroud which directs a cooling air flow to at least a portion of a pump of the pump assembly. The compressor assembly can have an air ducting shroud having at least one partition which directs a cooling air flow.
The compressor assembly can have an air ducting shroud having a conduit adapted to direct a cooling air flow to a cylinder head of the pump assembly. The compressor assembly can have an air ducting shroud which directs cooling air to at least a portion of a cylinder of the pump assembly. The compressor assembly can have an air ducting shroud which encases a motor and directs a first cooling air flow to a first stator coil of a motor and which directs a second cooling air flow to a second stator of a motor and a third cooling air flow to a cylinder head of the pump assembly.
The compressor assembly can have a heat transfer rate from the pump assembly having a value in a range of 60 BTU/min or greater when the compressor is in a compressing state.
The compressor assembly can have a cooling air flow rate having a value of 50 CFM or greater when the compressor is in a compressing state.
The compressor assembly can have a motor of the pump assembly, with a motor efficiency which is greater than 45 percent.
In an aspect, the compressor assembly can be cooled by a method having the steps of: providing a fan; providing a pump assembly; cooling the pump assembly with at least a portion of a cooling air flow provided by the fan when the compressor is in a compressing state; and operating the compressor at a sound level of less than 75 dBA.
The method of cooling a compressor assembly can also have the steps of: providing a motor of the pump assembly; providing a cylinder head of the pump assembly; providing a cooling air flow to cool both the motor and the cylinder head; and orienting the motor to such that a substantial portion of the cylinder head can receive at least a portion of cooling air which has not cooled the motor.
The method of cooling a compressor assembly can also have the steps of: providing an air ducting shroud having a plurality of conduits; and feeding a cooling air through the plurality of conduits to cool a pump assembly having the motor.
A compressor assembly can have a means for directing a plurality of cooling air flows to cool a pump assembly of the compressor assembly; and a means for dampening a noise from a compressor assembly to a sound level of 75 dBA or less.
The compressor can have a means for directing a cooling air flow to a cylinder head of the pump assembly from a fan, and a means for directing a cooling air flow from the fan to a motor of the pump assembly.
The compressor can have a means for directing a cooling air flow to a cylinder of the pump assembly.
The compressor can have a means for partitioning chambers within the compressor assembly such that at least one chamber has at least a portion of trapped air.
FIG. 22 is a view of the intake-side of the fan;
FIG. 23 is a first sectional view of the pump assembly;
FIG. 24 is a second sectional view of the pump assembly;
FIG. 25 is a sectional view of the pump assembly;
FIG. 26 is a sectional view of the motor and cooling air flow paths;
FIG. 27 is a cutaway sectional view of the air ducting shroud and cooling air plow paths;
FIG. 28 illustrates exhaust plow paths;
FIG. 29 is a view of exhaust venting;
FIG. 30 is a cross-sectional view of an exhaust chamber of the compressor assembly;
FIG. 31 is a front sectional view showing examples of cooling air plow paths; and
FIG. 32 is a top sectional view showing examples of cooling air plow paths.
Numeric values and ranges herein, unless otherwise stated, also are intended to have associated with them a tolerance and to account for variances of design and manufacturing, and/or operational and performance fluctuations. Thus, a number disclosed herein is intended to disclose values “about” that number. For example, a value X is also intended to be understood as “about X”. Likewise, a range of Y-Z is also intended to be understood as within a range of from “about Y-about Z”. Unless otherwise stated, significant digits disclosed for a number are not intended to make the number an exact limiting value. Variance and tolerance, as well as operational or performance fluctuations, are an expected aspect of mechanical design and the numbers disclosed herein are intended to be construed to allow for such factors (in non-limiting e.g., ±10 percent of a given value). This disclosure is to be broadly construed. Likewise, the claims are to be broadly construed in their recitations of numbers and ranges.
A cooling gas stream, such as cooling air stream 2000 (FIG. 3), can be drawn through intake ports 182 to feed fan 200. The cooling air stream 2000 can be divided into a number of different cooling air stream flows which can pass through portions of the compressor assembly and exit separately, or collectively as an exhaust air steam through the plurality of exhaust ports 31. Additionally, the cooling gas, e.g. cooling air stream 2000, can be drawn through the plurality of intake ports 182 and directed to cool the internal components of the compressor assembly 20 in a predetermined sequence to optimize the efficiency and operating life of the compressor assembly 20. The cooling air can be heated by heat transfer from compressor assembly 20 and/or the components thereof, such as pump assembly 25 (FIG. 3). The heated air can be exhausted through the plurality of exhaust ports 31.
In an embodiment, the outlet pressure of cooling air from the fan can be in a range of from 1 psig to 50 psig. In an embodiment, the fan 200 can be a low flow fan with which generates an outlet pressure having a value in a range of from 1 in of water to 10 psi. In an embodiment, the fan 200 can be a low flow fan with which generates an outlet pressure having a value in a range of from 2 in of water to 5 psi.
Depending upon the compressed gas output, the design rating of the motor 33 and the operating voltage, in an embodiment the motor 33 can operate at a value of rotation (motor speed) between 5,000 rpm and 20,000 rpm. In an embodiment, the motor 33 can operate at a value in a range of between 7,500 rpm and 12,000 rpm. In an embodiment, the motor 33 can operate at e.g. 11,252 rpm, or 11,000 rpm; or 10,000 rpm; or 9,000 rpm; or 7,500; or 6,000 rpm; or 5,000 rpm. The pulley 66 and the sprocket 49 can be sized to achieve reduced pump speeds (also herein as “reciprocation rates”, or “piston speed”) at which the piston 63 is reciprocated. For example, if the sprocket 49 can have a diameter of 1 in and the pulley 66 can have a diameter of 4 in, then a motor 33 speed of 14,000 rpm can achieve a reciprocation rate, or a piston speed, of 3,500 strokes per minute. In an embodiment, if the sprocket 49 can have a diameter of 1.053 in and the pulley 66 can have a diameter of 5.151 in, then a motor 33 speed of 11,252 rpm can achieve a reciprocation rate, or a piston speed (pump speed), of 2,300 strokes per minute.
The compressor assembly 20 can be designed to accommodate a variety of types of motor 33. The motors 33 can come from different manufacturers and can have horsepower ratings of a value in a wide range from small to very high. In an embodiment, a motor 33 can be purchased from the existing market of commercial motors. For example, although the housing 21 is compact, in an embodiment it can accommodate a universal motor, or other motor type, rated, for example, at ½ horsepower, at ¾ horsepower or 1 horsepower by scaling and/or designing the air ducting shroud 485 to accommodate motors in a range from small to very large.
FIG. 7 also provides a view of the feed air system 905. The feed air system 905 can feed a feed air 990 through a feed air port 952 for compression in the pump cylinder 60 of pump assembly 25. The feed air port 952 can optionally receive a clean air feed from an inertia filter 949 (FIG. 8). The clean air feed can pass through the feed air port 952 to flow through an air intake hose 953 and an intake muffler feed line 898 to the intake muffler 900. The clean air can flow from the intake muffler 900 through muffler outlet line 902 and cylinder head hose 903 to feed pump cylinder head 61. Noise can be generated by the compressor pump, such as when the piston forces air in and out of the valves of valve plate assembly 62. The intake side of the pump can provide a path for the noise to escape from the compressor which intake muffler 900 can serve to muffle.
FIG. 16A is a perspective view of sound control chambers with an air ducting shroud 485. FIG. 16A illustrates the placement of air ducting shroud 485 in coordination with for example the fan chamber 550, the pump sound control chamber 491, the exhaust sound control chamber 555, and the upper sound control chamber 480.
The compressor assembly 20 can have noise emissions reduced by, for example, a slower fan and/or slower motor speeds, use of a check valve muffler, use of tank vibration dampeners, use of tank sound dampeners, use of a tank dampening ring, use of tank vibration absorbers to dampen noise to and/or from the tank walls which can reduce noise. In an embodiment, a two stage intake muffler can be used on the pump. A housing having reduced or minimized openings can reduce noise from the compressor assembly. As disclosed herein, the elimination of line of sight to the fan and other components as attempted to be viewed from outside of the compressor assembly 20 can reduce noise generated by the compressor assembly. Additionally, routing cooling air through ducts, using foam lined paths and/or routing cooling air through tortuous paths can reduce noise generation by the compressor assembly 20.
Additionally, noise can be reduced from the compressor assembly 20 and its sound level lowered by one or more of the following: employing slower motor speeds, using a check valve muffler and/or using a material to provide noise dampening of the housing 21 and its partitions and/or the compressed air tank 150 heads and shell. Other noise dampening features can include one or more of the following and be used with or apart from those listed above: using a two-stage intake muffler in the feed to a feed air port 952, elimination of line of sight to the fan and/or other noise generating parts of the compressor assembly 20, a quiet fan design and/or routing cooling air routed through a tortuous path which can optionally be lined with a sound absorbing material, such as a foam. Optionally, fan 200 can be a fan which is separate from the shaft 43 and can be driven by a power source which is not shaft 43.
FIG. 21 is a table containing a third example of performance characteristics of an example compressor assembly 20. In the Example of FIG. 21, a compressor assembly 20, having an air ducting shroud 485, a dampening ring 700, an intake muffler 900, four sound control chambers, a fan cover, four foam sound absorbers and a tank seal 600 exhibited the performance values set forth in FIG. 21.
The compressor assembly 20, which is driven by an electric motor, can generate heat in the motor windings, as well as in the pump cylinder 60 where the air is compressed. Performance can be enhanced and efficiency gained by dissipating heat produced in the motor 33 and pump cylinder 60. Heat dissipation, can be achieved by forced air cooling. In an embodiment, forced air cooling is achieved by a cooling air flow from the fan 200.
The air ducting shroud 485 can be used to provide a flow of cooling gas, such as air, to the pump assembly 25 which can have a motor 33, a pump 91 (FIG. 9) and the fan 200. The pump assembly 25 can compress a gas such as air. The air ducting shroud 485 can provide ducted air flow which can cool both the pump 91 and motor 33 efficiently. In an embodiment, the air ducting shroud 485 can be used to form one duct or a plurality of ducts which can direct cooling air from the fan 200 to one or a plurality of components of the pump assembly 25, such at to the pump 91 and motor 33.
In an embodiment, the motor 33 can be positioned to place the motor field windings, such as upper stator coil 40 and lower stator coil 41, at an orientation orthogonal to the cylinder head 61 (FIG. 27) to not substantially interfere with, or cause undesired choking, or compete for, cooling air flow to the cylinder head 61. The orientation of the field windings eliminates the need for these components to compete for the same cooling air. An orientation in which the motor field windings and/or motor do not substantially interfere with, or cause undesired choking of, or fight for, cooling air flow to the cylinder head 61 achieves efficient heat transfer and cooling air flow to portions of the pump assembly 25, such as the motor 33 and the cylinder head 61. Orienting the motor to allow an increased air flow to the head increases heat transfer and cooling to the cylinder head 61 and/or pump cylinder 60 and/or pump 91.
In an embodiment, the above-mentioned advantages can be achieved by arranging the motor field windings, such as the upper stator coil 40 and the lower stator coil 41, so they are offset from and/or not lined up with the cylinder head 61 (FIG. 27). Offsetting of the motor field windings from the cylinder head 61 can at least in part eliminate blocking or choking of the cylinder head 61 from cooling air flow. Such offsetting can allow ample cooling air flow to the motor field windings and the pump 91 concurrently. In this arrangement, both the pump and motor can be cooled by cooling air flow from a single fan 200. Additionally, this configuration allows for the use of a single fan having a low rate of flow to cool both of the pump 91 and the motor 33, and/or optionally the pump assembly 25. In an embodiment, the pump assembly 25 can be cooled by a single fan 200.
When mounting an air compressor in a housing, adequate cooling can affect the operating life of a compressor assembly 20 and the motor 33. Sources of heat in the motor 33 include but are not limited to the commutator 51 (FIG. 3), the first stator coil 40, the second stator coil 41, and coils in the rotor 50 (FIG. 3). Heat can be produced by the air as it is compressed in pump 91 and by the drive belt 65 (FIG. 3). The fan blade 205 can establish a forced flow of cooling air through the housing 21. According to one feature of the invention, the air ducting shroud 485 can separate the cooling air into a number of streams to cool these components of the compressor assembly 20.
In an embodiment, housing 21 can encase an air ducting shroud 485 (FIG. 2) which can have a number of pathways for guiding the cooling air from the fan 200. In a non-limiting example, the compressor assembly 20 cooling air stream 2000 is drawn into the fan 200 through the plurality of intake slots 182, and is driven into the compressor assembly as fan effluent stream 193 by the plurality of fan blades 205.
In an embodiment, the compressor assembly 20 uses pathways to direct the flow of cooling air to locations, such as for example to cool the pump 91 and the motor 33. Cooling the pump 91 and the motor 33 allows each to operate with improved efficiency. A pump cooling path for the pump assembly 25 can be created by forming an internal cast opening in the air ducting shroud 485.
In an embodiment, the cooling air flow can be divided into a number of cooling air flows (also herein as “segments”). In an embodiment, the flow paths can be of a size which reduces back pressure and avoids choking cooling air flow.
In an embodiment, the fan effluent stream 193 cooling air flow can be divided into two cooling air flows, a first cooling air flow (also herein as “segment 1”) and a second cooling air flow (also herein as “segment 2”). In the two cooling air flow embodiment, one of the cooling air flows can flow across the bottom field winding and the other cooling air flow can flow across the top field winding and the cylinder head 61 area of pump 91.
FIG. 22 is another embodiment in which the cooling air flow can be divided into three cooling air flows (three cooling air segments).
The example of FIG. 22 illustrates a fan 200 which can feed ambient air as cooling air into the air ducting shroud 485. The cooling air flow can be divided into at least three (3) cooling air flows. In an embodiment, the cooling air flow can be divided into a first cooling air flow (also herein as “segment 1”), a second cooling air flow (also herein as “segment 2”) and a third cooling air flow (also herein as “segment 3”). Respectively, FIG. 22 designates these cooling air flows representatively as “1”, “2” and “3”.
As illustrated in FIG. 22, the cooling air stream 2000 which passes through the fan 200 becomes the fan effluent stream 193 (FIG. 3) which can be separated internally into a plurality of cooling air flows, e.g. three or more cooling air flows stream. In FIG. 22, the fan effluent stream 193 can be partitioned into at least three streams as shown by the partition lines and three stream partition designations, i.e. “1”, “2” and “3”. In an embodiment, a cooling air flow 1 (“segment 1” of FIG. 22) can at least in part feed an upper motor stream 270 (FIG. 23). A cooling air flow 2 (“segment 2” of FIG. 22) can at least in part feed a lower motor stream 280 (FIG. 27). A cooling air flow 3 (“segment 3” of FIG. 22) can at least in part feed a pump stream 254 (FIG. 23).
The partition lines shown in FIG. 22 are exemplary in nature and the actual flow division of the fan caused by the air ducting shroud 485 will occur in accordance with the mechanical design of the air ducting shroud 485 and the fluid dynamics of the flow streams and the open paths which can exist.
In the embodiment disclosed herein, the cooling design of the compressor assembly 20 can control a temperature rise of the motor that meets or exceeds that required by UL 1450 (which is a standard set by UL LLC, 333 Pfingsten Road Northbrook, Ill. 60062-2096).
FIG. 23 is a first sectional view of the pump assembly showing the upper motor stream 270 cooling the fan-side of the upper stator coil 40. The lower motor stream 280 is also illustrated cooling the fan-side of the lower stator coil 41.
Electricity flowing through the field windings of the motor 33 generates heat in the motor. The air ducting shroud 485 can direct the cooling air into the areas heated by the heat generated in the motor 33. The sides of the motor that do not contain field windings can be blocked off (fully or partially depending on need) to force more air across the other two sides of the motor where the field windings are located, as well as into conduit 253. In this example, fan effluent stream 193 is split into three cooling air flow paths and each flow path is directed to one of at least three areas that need cooling, such as the two sides of the motor having stator coils (upper stator coil 40 and lower stator coil 41) and the pump 91 area having cylinder head 61 and pump cylinder 60. In an embodiment, the stream which can cool the cylinder head 61 can also cool the pump cylinder 60.
In an embodiment, the upper motor stream 270 can flow across at least a portion of the upper stator coil 40; the lower motor stream 280 can flow across at least a portion of the lower stator coil 41; and a conduit air stream 254 can flow across the cylinder head 61 and the pump cylinder 60 of the pump 91.
FIG. 27 illustrates the upper coil centerline 204 intersecting head centerline 202 at angle 207 which is 90 degrees. The lower coil centerline 206 is illustrated to intersect head centerline 202 at angle 207 which is 90 degrees. For illustrative purposes, this configuration can form the triangle 209 among at least a portion of the respective motor coils and head centerline 202 as shown in FIG. 27. Such configuration allows for easy passage of cooling air and separation of the cooling air blown by the fan.
FIG. 23 illustrates an embodiment having the fan effluent stream 193 which is separated into a upper motor stream 270, a lower motor stream 280 and a conduit air stream 254. The upper motor stream 270 can flow through the upper motor path 268 to cool the upper stator coil 40. The lower motor stream 280 can flow through lower motor path 278 to cool the lower stator coil 41. The conduit air stream 254 can flow through the conduit 253 to cool the cylinder head 61 and the pump cylinder 60.
FIG. 23 illustrates a front blocking partition 115 which blocks air flow along the front motor surface 486 of the motor 33. FIG. 23 also illustrates a rear blocking partition 116 which blocks air flow along the rear motor surface 488 of the motor 33. The blocking partition 115 and the blocking partition 116 can provide resistance which can force the cooling air to pass through the upper motor path 268 and the lower motor path 278, as well as through conduit 253 having conduit flow path 255.
In the example embodiment of FIG. 23, upper motor path 268 can be a passageway formed from surfaces of the motor 33 and the air ducting shroud 485. For example, upper motor path 268 can have a portion of the upper motor block surface 58 and a portion of the upper inside surface 487 of the air ducting shroud 485 (also herein as “motor cover 485”). In this example, the lower motor path 278 can be a passageway formed from e.g. a portion of the lower motor block surface 59 and a portion of the lower inside surface 489 of air ducting shroud 485.
In this embodiment, the air ducting shroud 485 can form the conduit 253 having the conduit flow path 255 and can have at least a portion which flows through the conduit 253.
FIG. 24 is a sectional view of a perspective of the fan-side of the motor in which the upper motor stream 270 can flow through the upper motor path 268, the lower motor stream 280 can flow through the lower motor path 278 and the conduit air stream 254 can flow the through the conduit 253.
FIG. 24 also is a cross-sectional view of the motor 33 and the conduit 253. In the example of FIG. 24, the blocking partitions 115 and the blocking partition 116 can force the cooling air to pass through the upper motor path 268, the lower motor path 278 and the conduit 253. In the embodiment illustrated in FIG. 24, the front blocking partition 115 and the rear blocking partition 116 are illustrated as blocking the flow of air along the front motor surface 490 and rear motor surface 492. The front blocking partition 115 can block the formation of an air flow between the front motor surface 490 and the front inside surface 486 of the air ducting shroud 485. The rear blocking partition 116 can block the formation of air flow between the rear motor surface 492 and the rear inside surface 488 of air ducting shroud 485. When the front blocking partition 115 and the rear blocking partition 116 are used, the fan effluent stream 193 can be partitioned to the cool the motor 33 (FIG. 3) and provide flow at least through upper motor path 268, the lower motor path 278 and the conduit flow path 255.
FIG. 25 is a sectional view of the pump assembly 25. The upper motor stream 270 can flow through the upper motor path 268. The lower motor stream 280 can flow through lower motor path 278. The conduit air stream 254 can flow through conduit 253 of air ducting shroud 485. In the example of FIG. 25, the flow of the conduit air stream 254 over cylinder head 61 can become a head air stream 256 as it contacts and flows across the cylinder head 61.
Optionally, the conduit 253 can extend to cover at least a portion of cylinder head 61. Optionally, the conduit 253 can be formed to provide cooling to at least a portion of the pump 91, such as the pump cylinder 60 and/or the cylinder head 61.
As shown in FIG. 26, an upper motor path 268 is formed between the upper stator portion of the motor and the inner diameter of the air ducting shroud 485 and a lower motor path 278 is formed between the lower stator portion of the motor and the inner diameter of the air ducting shroud 485. A motor gap 240 can extend in an axial direction through the motor 33 between the stator and the rotor. A portion of the air delivered by the fan blade 205 can flow though the motor air gap 240. In an embodiment, the cooling air can flow along a path in example sequence over the commutator 51 and brush assembly, then through the motor air gap 240, then over at least a portion of the pump cylinder 60 and through the plurality of exhaust slots 31. In an embodiment, this first flow of air can accept heat transfer from at least the motor 33, and then optionally at least the pump cylinder 60 and the cylinder head 61.
FIG. 26 is a sectional view of the motor and cooling air flow paths; showing cooling air which can flow through motor air gap 240 and flow across the upper stator coil 40 and the lower stator coil 41. The fan can direct some air to travel through the motor air gap 240 between the armature and the electric field to help cool the armature windings.
FIG. 27 is a cutaway sectional view of the air ducting shroud and cooling air flow.
As shown in FIG. 27, the upper motor stream 270 can flow through the upper motor path 268. The lower motor stream 280 can flow through lower motor path 278. FIG. 27 also illustrates a conduit air stream 254 which flows through conduit 253. A portion of the conduit air stream 254 can feed the pump stream 258 which separates from conduit stream 254 to cool the pump cylinder 60 of the pump 91. FIG. 28 also illustrates that the portion of the conduit air stream which does not become the pump stream 258 becomes the head air stream 256 which flows to cool cylinder head 61.
FIG. 27 also illustrates that the cylinder air stream 258 can separate from the pump air stream 254 into a first cylinder air stream 260 and a second cylinder air stream 262 to cool pump cylinder 60. The pump stream 258 can optionally be split as it passes though a plurality of optional ports. In the example of FIG. 27 pump stream 258 can split into a first cylinder air stream 260 which can flow through a first cylinder cooling port 261 and a second cylinder air stream 262 can flow through a second cylinder cooling port 259. The first cylinder air stream 260 and the second cylinder air stream 262 can cool at least pump cylinder 60.
In an embodiment, the fan effluent stream 193 can also supply flow to an upper motor stream 270 through upper motor path 268 and a lower motor stream 280 through lower motor path 278.
In an embodiment, the motor can be cooled at least in part by an upper motor stream 270 which can flow through an upper motor path 268. Additionally, the motor can be cooled at least in part by a lower motor stream 280 which can flow through lower motor path 278.
In an embodiment, at least a portion of the head air stream 256 flows over the cylinder head 61. Additionally, at least a portion of the pump cooling path can guide a portion the cooling air over the cylinder head 61 and pump cylinder 60. Also, a first cylinder air stream 258 can flow over at least a portion of pump cylinder 60 and can feed at least a portion of second cylinder air stream 262 which can also feed at least a portion of a second cylinder air stream 260 which can flow over at least a portion of pump cylinder 60.
FIG. 28 illustrates the exhaust flow paths. FIG. 28 is a pump-side view which illustrates the exhaust flow from the head air stream 256 as cylinder head exhaust air stream 296. The head exhaust air stream 296 can become an exhaust air stream 299.
FIG. 28 illustrates that the first cylinder air stream 260 (FIG. 28) can become a first cylinder exhaust air stream 289 which can become a cylinder exhaust air stream 295. The second cylinder air stream 262 (FIG. 28) can become a second cylinder exhaust air stream 291 which can become a cylinder exhaust air stream 295. The cylinder head exhaust air stream 295 can also become an exhaust air stream 299.
In the example embodiment illustrated in FIG. 28, the upper motor stream 270 can flow through the upper motor path 268, then across upper stator coil 40 and becomes upper winding exhaust 293. The lower motor stream 280 can flow through the lower motor path 278, then across lower stator coil 41 and becomes lower winding exhaust 294.
The upper motor stream 270 can become an upper winding exhaust air stream 293 which can become a windings exhaust air stream 297. The lower motor stream 280 can become a lower winding exhaust air stream 294 which can become a windings exhaust air stream 297. The windings exhaust air stream 297 can become an exhaust air stream 299.
FIG. 28 illustrates the flow of the exhaust air stream 299. In an embodiment, the exhaust air stream 299 is a combined exhaust air stream of the exhausts streams which have passed over portions of the motor or portions of the pump. In an embodiment, the exhaust air stream 299 is a combined exhaust air stream of the exhaust flowing from upper motor path 268, lower motor path 278 and conduit 253.
FIG. 29 illustrates a view of exhaust venting. FIG. 29 illustrates the head exhaust air stream 296 becoming an exhaust air stream 299 and exiting the compressor assembly 20 through a plurality of the exhaust air slots 31. The cylinder exhaust air 295 can become an exhaust air stream 299 and can exit the compressor assembly 20 through the exhaust air slots 31. The windings exhaust air stream 297 can become an exhaust air stream 299 and can exit the compressor assembly 20 through the exhaust air slots 31. Optionally, one or a plurality of louvers 298 can be used in conjunction with the exhaust air slots 31. The louvers 298 can eliminate an operator's line-of-sight to the pump assembly 25 and/or to one or more noise making parts.
FIG. 30 is a cross-sectional view of the exhaust chamber of the compressor assembly. In the embodiment of FIG. 30, a plurality of louvers 298 can be used in conjunction with the exhaust air slots 31.
FIG. 31 is a front sectional view showing examples of cooling air plow paths.
Cooling air can pass on the two sides of the motor with the field coils. Openings can be used to force air across the windings. Air flow can be blocked on the two sides of the motor having no field coils along those two sides. Cooling air from fan can flow across head and cylinder area.
a pump assembly including a motor having a plurality of motor surfaces, a motor shaft having a longitudinal axis, and a motor speed of 5,000 rpm or greater;
an air ducting shroud which directs cooling air to at least a portion of the motor and which is adapted to dampen a noise from the pump assembly, the air ducting shroud having:
a front inside surface and a rear inside surface;
a front blocking partition integrally molded with the front inside surface and in contact with a front motor surface that is parallel to the longitudinal axis of the motor; and
a rear blocking partition integrally molded with the rear inside surface and in contact with a rear motor surface that is parallel to the longitudinal axis of the motor, the rear motor surface being on a laterally opposing side from the front motor surface,
wherein the blocking partitions block the formation of an airflow between the motor and the front and rear inside surfaces and force the air that is flowing over an outer surface of the motor to only flow along the outer surfaces that are perpendicular to the front and rear motor surfaces; and
a sound level having a value of 75 dBA or less when the compressor is in a compressing state.
2. The compressor assembly according to claim 1, wherein the air ducting shroud encases at least a portion of the fan.
3. The compressor assembly according to claim 1, wherein the air ducting shroud encases at least a portion of the motor.
4. The compressor assembly according to claim 1, wherein the air ducting shroud comprises a conduit which directs a cooling air flow to a cylinder head of the pump assembly.
5. The compressor assembly according to claim 1, wherein the air ducting shroud directs a cooling air flow to at least a portion of a pump of the pump assembly.
6. The compressor assembly according to claim 1, wherein the air ducting shroud directs cooling air to at least a portion of a cylinder of the pump assembly.
7. The compressor assembly according to claim 1, wherein the air ducting shroud further comprises a conduit adapted to direct a cooling air flow to a cylinder head of the pump assembly.
8. The compressor assembly according to claim 1, wherein the air ducting shroud has at least one partition which directs a cooling air flow.
9. The compressor assembly according to claim 1, wherein the air ducting shroud encases the motor and directs a first cooling air flow to a first stator coil of the motor and which directs a second cooling air flow to a second stator of the motor and a third cooling air flow to a cylinder head of the pump assembly.
10. The compressor assembly according to claim 1, further comprising a heat transfer rate from the pump assembly having a value of 60 BTU/min or greater when the compressor is in a compressing state.
11. The compressor assembly according to claim 1, further comprising a cooling air flow rate having a value of 50 CFM or greater when the compressor is in a compressing state.
12. The compressor assembly according to claim 1, wherein the motor has a motor efficiency greater than 45 percent.
13. The compressor assembly according to claim 1, wherein the front blocking partition and the rear blocking partition contact front and rear surfaces of the motor.
14. The compressor assembly according to claim 1, wherein the front blocking partition and the rear blocking partition are integrally formed with the outer perimeter of the air ducting shroud.
15. A method of cooling a compressor assembly, comprising the steps of:
providing a pump assembly including a motor having a plurality of motor surfaces, a motor shaft having a longitudinal axis and a motor speed of 5,000 rpm or greater;
providing an air ducting shroud which directs a cooling air flow, the air ducting shroud having:
wherein the blocking partitions block the formation of an airflow between the motor and the front and rear inside surfaces of the air ducting shroud and force the air that is flowing over an outer surface of the motor to only flow along the outer surfaces of the motor that are perpendicular to the front and rear motor surfaces;
cooling the pump assembly with at least a portion of the cooling air flow provided by the fan when the compressor is in a compressing state; and
operating the compressor at a sound level of less than 75 dBA.
16. The method of cooling a compressor assembly according to claim 15, further comprising the steps of:
providing a cylinder head of the pump assembly;
providing a cooling air flow to cool both the motor and the cylinder head; and
orienting the motor such that a portion of the cylinder head can receive at least a portion of cooling air which has not cooled the motor.
17. The method of cooling a compressor assembly according to claim 16, wherein the step of providing an air ducting shroud comprises providing an air ducting shroud having a plurality of conduits, and
feeding a cooling air through the plurality of conduits to cool the motor.
US13609331 2011-09-13 2012-09-11 Air ducting shroud for cooling an air compressor pump and motor Active 2033-09-25 US9458845B2 (en)
US201161534046 true 2011-09-13 2011-09-13
US201161534015 true 2011-09-13 2011-09-13
US201161534001 true 2011-09-13 2011-09-13
US201161534009 true 2011-09-13 2011-09-13
US201161533993 true 2011-09-13 2011-09-13
US13609331 US9458845B2 (en) 2011-09-13 2012-09-11 Air ducting shroud for cooling an air compressor pump and motor
US13987844 US20140037425A1 (en) 2011-09-13 2013-09-09 Air ducting shroud for cooling an air compressor pump and motor
EP20130183932 EP2706234A1 (en) 2012-09-11 2013-09-11 Air ducting shroud for cooling an air compressor pump and motor
US13609343 Continuation-In-Part US20130065503A1 (en) 2011-09-13 2012-09-11 Air Ducting Shroud For Cooling An Air Compressor Pump And Motor
US20130064641A1 true US20130064641A1 (en) 2013-03-14
US9458845B2 true US9458845B2 (en) 2016-10-04
ID=46826354
US13609331 Active 2033-09-25 US9458845B2 (en) 2011-09-13 2012-09-11 Air ducting shroud for cooling an air compressor pump and motor
US13609345 Active US8967324B2 (en) 2011-09-13 2012-09-11 Compressor housing having sound control chambers
US13609355 Active US9127662B2 (en) 2011-09-13 2012-09-11 Tank dampening device
US13609359 Active US8851229B2 (en) 2011-09-13 2012-09-11 Tank dampening device
US13609343 Abandoned US20130065503A1 (en) 2011-09-13 2012-09-11 Air Ducting Shroud For Cooling An Air Compressor Pump And Motor
US13609363 Active US8770341B2 (en) 2011-09-13 2012-09-11 Compressor intake muffler and filter
US13609349 Pending US20130064689A1 (en) 2011-09-13 2012-09-11 Method Of Reducing Air Compressor Noise
US14493484 Active US9181938B2 (en) 2011-09-13 2014-09-23 Tank dampening device
US14499375 Active US9097246B2 (en) 2011-09-13 2014-09-29 Tank dampening device
US14813176 Active US9670920B2 (en) 2011-09-13 2015-07-30 Tank dampening device
US15822015 Active US10012223B2 (en) 2011-09-13 2017-11-24 Compressor housing having sound control chambers
US (11) US9458845B2 (en)
EP (7) EP2570664A3 (en)
CN (7) CN203067239U (en)
CN103994053A (en) * 2014-04-16 2014-08-20 浙江鸿友压缩机制造有限公司 Cooling layout structure of direct-connection-type oil-free compressor
DE102014113598A1 (en) * 2014-09-19 2016-03-24 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Multi-stage piston compressor with an external cooling air passage
CN104481859B (en) * 2014-09-19 2017-02-15 燕山大学 A pressure self-feedback type axial piston pump turbine inlet pulsation absorbing regulator
CN205592093U (en) * 2015-03-11 2016-09-21 周文三 Can carry out radiating pump equipment of motor group structure
CN105041607A (en) * 2015-08-17 2015-11-11 奉化市必达机械制造有限公司 Air cooling air compressor
KR20170085438A (en) * 2016-01-14 2017-07-24 웬-산 초우 Improved air discharging structure in the compressible cylinder of an air compressor
KR20170085963A (en) * 2016-01-15 2017-07-25 웬-산 초우 Improved air discharging structure in the compressible cylinder of an air compressor
KR20170101111A (en) * 2016-02-26 2017-09-05 웬-산 초우 Improved air discharging structure in the compressible cylinder of an air compressor
US6435076B1 (en)
US5311090A (en) 1992-03-20 1994-05-10 Ferlatte Andre A Motor protection device
US1469201A (en) 1922-11-09 1923-09-25 Whitted Howard Ferris Automatic inflating device
FR919265A (en) * 1945-08-10 1947-03-04 Frame for air compressor
US3370608A (en) * 1966-08-12 1968-02-27 Whirlpool Co Liquid handling apparatus with pump means having mount and seal
US3591315A (en) * 1969-11-26 1971-07-06 Gen Motors Corp Reciprocal compressor and accumulator for automatic vehicle leveling system
DE2751298A1 (en) 1977-11-16 1979-05-17 Kates Co W A Spring loaded fluid flow regulator - has easily dismantled flange connected sections to aid cleaning
CA1267397A (en) * 1984-01-13 1990-04-03 Thomas E. Grime Tank mounting for compressor and motor
US4759422A (en) * 1987-05-04 1988-07-26 Duo-Vac Inc. Silencer for a cooling fan of a vacuum cleaning system
JPS6480793A (en) 1987-09-21 1989-03-27 Matsushita Refrigeration Rotary compressor
US4877106A (en) * 1988-04-29 1989-10-31 Carrier Corporation Sound-attenuating discharge apparatus for a packaged terminal air conditioner
KR940003845Y1 (en) 1991-12-28 1994-06-15 이헌조 Compressor
DE4416555A1 (en) * 1994-05-11 1995-11-16 Pampel Steffen Dipl Ing Compressed air reservoir
JP2895407B2 (en) * 1994-12-01 1999-05-24 本田技研工業株式会社 Intake silencer
KR100288872B1 (en) * 1998-01-20 2001-02-12 Samsung Electronics Co Ltd Noise reduction apparatus for air conditioner outdoor unit
US6102679A (en) * 1998-03-12 2000-08-15 Brown; Gerald E. Air compressor
DE19908308A1 (en) 1999-02-26 2000-08-31 Boge Kompressoren compressors
DE10114327C2 (en) 2001-03-23 2003-07-03 Danfoss Compressors Gmbh suction silencer
JP4621388B2 (en) 2001-08-29 2011-01-26 パイロットインキ株式会社 Portable compressor
KR100461231B1 (en) 2002-11-28 2004-12-17 삼성광주전자 주식회사 Suction muffler for compressor
DE60206517T2 (en) * 2002-12-20 2006-06-22 Delphi Technologies, Inc., Troy A vibration isolating fuel pump unit
DE10323526B3 (en) 2003-05-24 2005-02-03 Danfoss Compressors Gmbh A suction muffler for a hermetic refrigerant compressor
US20050247750A1 (en) 2003-07-31 2005-11-10 Burkholder Robert F Integrated air tool and pressure regulator
JP4752255B2 (en) * 2004-12-06 2011-08-17 パナソニック株式会社 Hermetic compressor
EP1828603B1 (en) * 2004-12-22 2008-04-30 ACC Austria GmbH Hermetic refrigerant compressor
DE102006025085A1 (en) * 2006-05-30 2007-12-06 Schneider Druckluft Gmbh compressor device
CN101144668A (en) * 2006-09-15 2008-03-19 乐金电子(天津)电器有限公司 Liquid tank vibration damper
US8282363B2 (en) * 2007-04-03 2012-10-09 Techtronic Power Tools Technology Limited Portable air compressor
US20090050219A1 (en) 2007-08-21 2009-02-26 Briggs And Stratton Corporation Fluid compressor and control device for the same
US7543683B2 (en) * 2007-11-06 2009-06-09 Honda Motor Co., Ltd. Vehicle resonator structure and attachment method
JP2009121244A (en) * 2007-11-12 2009-06-04 Honda Motor Co Ltd Soundproof enclosed type generator
US8235683B2 (en) * 2007-12-06 2012-08-07 Panasonic Corporation Hermetic compressor
KR101386479B1 (en) 2008-03-04 2014-04-18 엘지전자 주식회사 Muffler for compressor
WO2009110060A1 (en) * 2008-03-04 2009-09-11 東京濾器株式会社 Sound-deadening structure of vent tube and sound-deadening structure of case
JP5524957B2 (en) 2008-06-18 2014-06-18 ワールプール，ソシエダッド アノニマ Compressor noise muffler and the compressor
KR101328226B1 (en) 2008-10-22 2013-11-14 엘지전자 주식회사 Suction muffler for hermetic type compressor
JP5338355B2 (en) * 2009-02-13 2013-11-13 パナソニック株式会社 Hermetic compressor and a refrigeration apparatus
CN201526435U (en) * 2010-02-04 2010-07-14 浙江鸿友压缩机制造有限公司 Cooling structure for straight connecting type air compressor crane case
CN101737303B (en) * 2010-02-04 2012-08-08 浙江鸿友压缩机制造有限公司 Cooling structure of crankcase of directly coupled type air compressor
US9458845B2 (en) * 2011-09-13 2016-10-04 Black & Decker Inc. Air ducting shroud for cooling an air compressor pump and motor
JP1080793A (en)
US6554583B1 (en) * 1998-09-29 2003-04-29 Hans-Georg G. Pressel Swash plate compressor with reciprocal guide assembly
US20130065503A1 (en) 2013-03-14 application
US20130064641A1 (en) 2013-03-14 application
US9127662B2 (en) 2015-09-08 grant
EP2570668A2 (en) 2013-03-20 application
EP2570664A2 (en) 2013-03-20 application
US20150152857A1 (en) 2015-06-04 application
CN203067237U (en) 2013-07-17 grant
EP2570668A3 (en) 2017-03-08 application
US20130064689A1 (en) 2013-03-14 application
EP2570667A2 (en) 2013-03-20 application
EP2570664A3 (en) 2017-03-08 application
US8851229B2 (en) 2014-10-07 grant
US20130062141A1 (en) 2013-03-14 application
EP2570665A3 (en) 2016-11-30 application
US20130064643A1 (en) 2013-03-14 application
CN202926558U (en) 2013-05-08 grant
US20180073495A1 (en) 2018-03-15 application
EP2570669A3 (en) 2017-03-15 application
US20150330380A1 (en) 2015-11-19 application
US20150016962A1 (en) 2015-01-15 application
US9181938B2 (en) 2015-11-10 grant
CN203067238U (en) 2013-07-17 grant
US9097246B2 (en) 2015-08-04 grant
EP2570666A2 (en) 2013-03-20 application
US20130062140A1 (en) 2013-03-14 application
US8967324B2 (en) 2015-03-03 grant
EP2570667A3 (en) 2017-03-22 application
EP2570666A3 (en) 2017-03-08 application
US20150016953A1 (en) 2015-01-15 application
EP2570670A2 (en) 2013-03-20 application
CN203067236U (en) 2013-07-17 grant
US20130064642A1 (en) 2013-03-14 application
EP2570669A2 (en) 2013-03-20 application
EP2570670A3 (en) 2017-03-22 application
CN203067240U (en) 2013-07-17 grant
US8770341B2 (en) 2014-07-08 grant
CN203067239U (en) 2013-07-17 grant
EP2570665A2 (en) 2013-03-20 application
CN203067216U (en) 2013-07-17 grant
US10012223B2 (en) 2018-07-03 grant
US9670920B2 (en) 2017-06-06 grant
US20060104833A1 (en) 2006-05-18 Fan guard having channel to direct cooling air to a piston cylinder
US7563077B2 (en) 2009-07-21 Quiet fluid pump
US20040123482A1 (en) 2004-07-01 Electric blower and vacuum cleaner using same
JP2007120505A (en) 2007-05-17 Motor-driven compressor for compressing refrigerant
CN201241828Y (en) 2009-05-20 Vacuum pump
EP2224136A2 (en) 2010-09-01 Air-cooled scroll compressor
US6793465B2 (en) 2004-09-21 Air treatment enclosure
KR100679857B1 (en) 2007-02-01 Housings for inverter integrate electric compressors
US20060204371A1 (en) 2006-09-14 Compressor assembly having an air-cooled electric motor
US20050232795A1 (en) 2005-10-20 Fluid pump, cooling apparatus and electrical appliance
JP2005076592A (en) 2005-03-24 Sound-insulated engine-driven work machine
CN1281535A (en) 2001-01-24 Motor-driven centrifugal air compressor with internal cooling airflow
US20050220614A1 (en) 2005-10-06 Fluid pump apparatus