US20060104833A1 - Fan guard having channel to direct cooling air to a piston cylinder - Google Patents
Fan guard having channel to direct cooling air to a piston cylinder Download PDFInfo
- Publication number
- US20060104833A1 US20060104833A1 US10/986,752 US98675204A US2006104833A1 US 20060104833 A1 US20060104833 A1 US 20060104833A1 US 98675204 A US98675204 A US 98675204A US 2006104833 A1 US2006104833 A1 US 2006104833A1
- Authority
- US
- United States
- Prior art keywords
- pump
- fan
- cooling flow
- channel
- fan guard
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
- 238000001816 cooling Methods 0.000 title claims abstract description 45
- 238000007906 compression Methods 0.000 description 5
- 229920006362 Teflon® Polymers 0.000 description 4
- 230000006835 compression Effects 0.000 description 4
- 239000000463 material Substances 0.000 description 3
- 229910000838 Al alloy Inorganic materials 0.000 description 2
- 230000008901 benefit Effects 0.000 description 2
- 229910052751 metal Inorganic materials 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 238000005273 aeration Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000001035 drying Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 239000000088 plastic resin Substances 0.000 description 1
- 229920000728 polyester Polymers 0.000 description 1
- 229920000642 polymer Polymers 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000011160 research Methods 0.000 description 1
- 239000010865 sewage Substances 0.000 description 1
- 238000009423 ventilation Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/06—Cooling; Heating; Prevention of freezing
- F04B39/066—Cooling by ventilation
Definitions
- the invention relates generally to the field of pumps, such as compressors and vacuum pumps, and more particularly, to a compressor having a fan guard with a channel to direct cooling air to a piston cylinder.
- Reciprocating piston or diaphragm pumps typically have a metal housing, for example, a cast aluminum alloy, in which bearings are mounted which journal the shaft which drives the pump.
- a metal housing is needed, particularly for larger pumps, to withstand the forces of driving the piston or diaphragm and containing the pressure exerted in the compression chamber of the pump.
- a rotary electric motor is usually used to drive these pumps and the motor requires cooling.
- the motor is provided between two housings, each of which is separate from the other and houses one compression chamber.
- the shaft of the motor is a through shaft so that each end of the shaft mounts one of the pistons or diaphragms that work to vary the volume of the compression chamber in the housing at the corresponding end of the shaft.
- a rotary fan blade is mounted to each end of the shaft to draw a flow of cooling air into the housing at that end and blow it onto the rotor and stator coils of the motor.
- the part of the housing in which the rotary fan blade is mounted circular and just slightly larger than the diameter of the fan blade.
- the clearance between the tips of the fan blades and the interior housing surface should be as small as possible because, if not, the air drawn into the housing by the fan blades will simply blow back out past the tips of the blade, and not be directed over the coils of the motor.
- the pump is contained inside of a separate enclosure, it may be permissible to leave open the end of the housing at which the fan blade is mounted.
- the end of the housing must be closed with a cover that permits air to be drawn into the housing, but prevents the insertion of larger objects or fingers. This cover, typically called a fan guard, should not deleteriously affect the operation of the fan nor add to the lateral size or detract from the appearance of the fan.
- the effectiveness of the cooling system in reducing the stator temperature of the motor affects the range of applications in which the pump may be employed.
- the voltage at which the motor is driven and the output pressure of the pump affect the amount of heat that is generated in the motor. More effective cooling expands the range of applications suitable for a given pump and motor.
- the motor is not the only temperature-sensitive component in a pump.
- Wobble pistons are sometimes used in oil-less air compressors and vacuum pumps.
- a wobble piston includes a peripheral seal on the piston head that engages the cylinder bore.
- the piston head and its connecting rod are fixed to each other, and the connecting rod is mounted on an eccentric on a shaft. As the eccentric is turned by the shaft, the wobble piston is moved in and out and “wobbles” from side to side.
- Wobble pistons typically employ a Teflon® or other similar material disc or cup which serves both as a guide for the wobble piston and as a pneumatic seal between the piston and the wall of the cylinder in which it moves.
- the working surface of the cylinder has a hardened polished surface, providing a smooth surface for cooperating with the Teflon® seal of the piston.
- the service life of the Teflon® material depends in part on the temperature of the cylinder with which the seal interfaces. A higher temperature typically corresponds to a shorter service life due to increased friction between the cup and the cylinder wall.
- the bearings used to support the motor shaft also have a service life determined at least in part by temperature. Generally, a higher bearing temperature equates to a shorter bearing service life.
- cooling efficiency not only affects the range of applications for a particular pump, but also the service life of temperature-sensitive components in the pump.
- the present invention addresses these problems.
- the present invention is directed generally to a fan guard that directs cooling air flow to a piston cylinder.
- a pump including a housing, a shaft supported by the housing, a piston assembly, a fan blade, and a fan guard.
- the piston assembly includes a piston cylinder and is operably coupled to the shaft.
- the fan blade is operable to generate cooling flow.
- the fan guard is mounted to the housing and includes a channel configured to direct at least a first portion of the cooling flow to the piston cylinder.
- the fan guard includes a front surface defining a cooling flow opening and sidewalls defining a channel having a first end proximate the cooling flow opening.
- a baffle is positioned proximate a second end of the channel.
- FIG. 1 is an isometric view of a pump in accordance with one embodiment of the present invention
- FIG. 2 is a partial cross section view of the pump of FIG. 1 ;
- FIG. 3 is an end view of the pump of FIG. 1 with the fan guard removed;
- FIG. 4 is an isometric back view of a fan guard employed in the pump of FIG. 1 .
- FIG. 1 illustrates a pump 10 of the invention having a motor 12 with a housing 14 at one end and a housing 16 at the other.
- the housings 14 , 16 are cast of aluminum alloy and are essentially identical.
- a head assembly 18 which includes head members 20 , 22 and connecting tubes 24 , 26 , is bolted to the housings 14 , 16 above respective compression chamber portions 28 , 30 of the housings 14 , 16 to help hold the housings 14 , 16 together and maintain their angular position with respect to each other.
- the pump 10 also includes fan guards 32 , one at each end, which are essentially identical to one another.
- the pump 10 of the present invention may be employed in a variety of applications, including but not limited to cable drying, sewage aeration, tire inflation, etc.
- FIGS. 2 and 3 a partial cross section view of the pump 10 and an end view of the pump 10 with the fan guard 32 removed are shown, respectively.
- the motor 12 has a shaft 34 which extends through it and into both housings 14 , 16 , nearly to the end of each respective housing 14 , 16 .
- both housings 14 , 16 are essentially identical, only the housing 14 is shown in FIG. 2 .
- Each end of the shaft 34 mounts a rotary fan blade 36 which is rotated by the shaft 34 within a fan cavity 37 defined by the housing 14 in a direction so as to draw air into each respective housing 14 , 16 and direct it over the coils of the motor 12 (i.e., an axial component of the cooling flow).
- the rotary fan blade 36 is secured to the shaft 34 using a spring clip 38 .
- the housings 14 , 16 are provided with ventilation slots 39 to allow the exhausting of cooling air.
- the housings 14 , 16 mount bearings 40 which journal the shaft 34 .
- the housings 14 , 16 also have openings (not shown) in them which provide for the axial through-flow of air so that air moved by the fan blade 36 reaches the coils of the motor 12 .
- the pump 10 includes a piston assembly 42 including a piston cylinder 44 and a piston head 46 operating within the piston cylinder 44 to compress the operating fluid (e.g., air) to provide the pumping action.
- the piston head 46 is coupled by a connecting rod 48 to an eccentric 50 fixed to the shaft 34 .
- the shaft 34 and attached eccentric 50 rotates causing the connecting rod 48 and piston head 46 to move within the piston cylinder 44 .
- a flapper valve (not shown) mounted to the valve plate 52 allows the air to enter the piston cylinder 44 on the downstroke of the piston cycle and seals to prevent air passage on the upstroke.
- the piston head 46 also includes a piston cup 54 constructed of Teflon® or other similar material that provides a sliding seal between the piston head 46 and the piston cylinder 44 .
- the piston cup 54 has a service life that may vary based on the temperature of the piston cylinder 44 , with a higher cylinder temperature resulting in a shorter service life.
- the fan guard 32 also directs cooling flow over the piston cylinder 44 to dissipate heat generated during the compression process.
- the housings 14 , 16 includes openings 56 (shown in FIG. 1 ) to allow the exhaust of cooling air directed over the piston cylinder 44 .
- FIG. 4 an isometric back view of the fan guard 32 is provided.
- the front surface of the fan guard 32 is visible in FIG. 1 .
- the fan guard 32 defines a cooling flow opening 57 in its front surface to provide for the passage of cooling flow past the fan guard 32 .
- the fan guard includes rib members 58 spanning the cooling flow opening 57 and support members 60 running perpendicular to the rib members 58 .
- the spacing and arrangement of the rib and support members 58 , 60 may vary depending on the particular implementation. In general, the rib and support members 58 , 60 are arranged to allow the passage of cooling flow, but to prevent foreign objects from entering the area proximate the moving rotary fan blade 36 .
- the fan guard 32 is made of a resilient plastic resin, such as a polyester polymer.
- the fan guard 32 includes a tab 62 that interfaces with a corresponding notch 64 (shown in FIG. 2 ) in the housing 14 to secure the bottom portion of the fan guard 32 to the housing 16 .
- Mounting holes 66 are defined in the fan guard 32 to allow the passage of screws for securing the fan guard 32 to the housing 14 via corresponding holes 68 (shown in FIG. 3 ) in the housing 14 . Any means may be used to secure the fan guard 32 to the housing 14 .
- the fan guard 32 includes sidewalls 70 that define a channel 72 .
- the channel 72 terminates in a baffle 74 that changes the direction of radial cooling flow generated by the rotary fan blade 36 to impinge on the piston cylinder 44 , as indicated by the arrow 76 shown in FIG. 2 .
- the sidewalls 70 also define a flared portion 78 that collects the radial air flow and directs the flow into the channel 72 .
- the rotary fan blade 36 includes an extended hub 80 that abuts the eccentric 50 to positively locate the rotary fan blade 36 along the shaft 34 within the fan cavity 37 .
- the rotary fan blade 36 is positioned to optimize the cooling provided to the piston cylinder 44 by the cooling flow redirected by the fan guard 32 .
- the optimal shaft position may be determined empirically and may vary depending on the particular geometry of the pump 10 .
- the rotary fan blade 36 extends axially beyond the fan cavity 37 defined by the housing 14 into the space bounded by the fan guard 32 . This position has been found to increase the effectiveness of the fan guard 32 in redirecting the radial air flow to cool the piston cylinder 44 .
- Redirecting cooling flow over the piston cylinder 44 reduces the operating temperature of the piston assembly 42 .
- the combination of the rotary fan blade 36 and fan guard 32 also reduces the temperature of the bearings 40 and the motor 12 . Such temperature reductions increase the operating lives of the piston cup 54 and the bearings 40 for a given set of operating conditions.
- the improved heat dissipation characteristics may also be employed to extend the operating range of the pump 10 to allow operation at higher pressures, different voltages, and/or lower frequency voltage inputs.
Abstract
Description
- Not applicable.
- Not applicable.
- The invention relates generally to the field of pumps, such as compressors and vacuum pumps, and more particularly, to a compressor having a fan guard with a channel to direct cooling air to a piston cylinder.
- Reciprocating piston or diaphragm pumps typically have a metal housing, for example, a cast aluminum alloy, in which bearings are mounted which journal the shaft which drives the pump. A metal housing is needed, particularly for larger pumps, to withstand the forces of driving the piston or diaphragm and containing the pressure exerted in the compression chamber of the pump.
- A rotary electric motor is usually used to drive these pumps and the motor requires cooling. In one such pump, the motor is provided between two housings, each of which is separate from the other and houses one compression chamber. The shaft of the motor is a through shaft so that each end of the shaft mounts one of the pistons or diaphragms that work to vary the volume of the compression chamber in the housing at the corresponding end of the shaft. Further out from where the piston or diaphragm is mounted, a rotary fan blade is mounted to each end of the shaft to draw a flow of cooling air into the housing at that end and blow it onto the rotor and stator coils of the motor.
- For cooling efficiency, it is desirable to make the part of the housing in which the rotary fan blade is mounted circular and just slightly larger than the diameter of the fan blade. The clearance between the tips of the fan blades and the interior housing surface should be as small as possible because, if not, the air drawn into the housing by the fan blades will simply blow back out past the tips of the blade, and not be directed over the coils of the motor. For applications in which the pump is contained inside of a separate enclosure, it may be permissible to leave open the end of the housing at which the fan blade is mounted. However, if the pump is going to be exposed or sold as a stand-alone product, the end of the housing must be closed with a cover that permits air to be drawn into the housing, but prevents the insertion of larger objects or fingers. This cover, typically called a fan guard, should not deleteriously affect the operation of the fan nor add to the lateral size or detract from the appearance of the fan.
- The effectiveness of the cooling system in reducing the stator temperature of the motor affects the range of applications in which the pump may be employed. The voltage at which the motor is driven and the output pressure of the pump affect the amount of heat that is generated in the motor. More effective cooling expands the range of applications suitable for a given pump and motor.
- The motor is not the only temperature-sensitive component in a pump. Wobble pistons are sometimes used in oil-less air compressors and vacuum pumps. A wobble piston includes a peripheral seal on the piston head that engages the cylinder bore. The piston head and its connecting rod are fixed to each other, and the connecting rod is mounted on an eccentric on a shaft. As the eccentric is turned by the shaft, the wobble piston is moved in and out and “wobbles” from side to side. Wobble pistons typically employ a Teflon® or other similar material disc or cup which serves both as a guide for the wobble piston and as a pneumatic seal between the piston and the wall of the cylinder in which it moves. The working surface of the cylinder has a hardened polished surface, providing a smooth surface for cooperating with the Teflon® seal of the piston. The service life of the Teflon® material depends in part on the temperature of the cylinder with which the seal interfaces. A higher temperature typically corresponds to a shorter service life due to increased friction between the cup and the cylinder wall.
- The bearings used to support the motor shaft also have a service life determined at least in part by temperature. Generally, a higher bearing temperature equates to a shorter bearing service life.
- Hence, cooling efficiency not only affects the range of applications for a particular pump, but also the service life of temperature-sensitive components in the pump. The present invention addresses these problems.
- The present invention is directed generally to a fan guard that directs cooling air flow to a piston cylinder.
- One aspect of the invention is seen in a pump including a housing, a shaft supported by the housing, a piston assembly, a fan blade, and a fan guard. The piston assembly includes a piston cylinder and is operably coupled to the shaft. The fan blade is operable to generate cooling flow. The fan guard is mounted to the housing and includes a channel configured to direct at least a first portion of the cooling flow to the piston cylinder.
- Another aspect of the present invention is seen in a fan guard. The fan guard includes a front surface defining a cooling flow opening and sidewalls defining a channel having a first end proximate the cooling flow opening. A baffle is positioned proximate a second end of the channel.
- Other objects, advantages and features of the present invention will become apparent from the following specification when taken in conjunction with the accompanying drawings.
- The invention may be understood by reference to the following description taken in conjunction with the accompanying drawings, in which like reference numerals identify like elements and in which:
-
FIG. 1 is an isometric view of a pump in accordance with one embodiment of the present invention; -
FIG. 2 is a partial cross section view of the pump ofFIG. 1 ; -
FIG. 3 is an end view of the pump ofFIG. 1 with the fan guard removed; and -
FIG. 4 is an isometric back view of a fan guard employed in the pump ofFIG. 1 . - While the invention is susceptible to various modifications and alternative forms, specific embodiments thereof have been shown by way of example in the drawings and are herein described in detail. It should be understood, however, that the description herein of specific embodiments is not intended to limit the invention to the particular forms disclosed, but on the contrary, the intention is to cover all modifications, equivalents, and alternatives falling within the spirit and scope of the invention as defined by the appended claims.
- While the present invention may be embodied in any of several different forms, the present invention is described here with the understanding that the present disclosure is to be considered as setting forth an exemplification of the present invention that is not intended to limit the invention to the specific embodiment(s) illustrated. Nothing in this application is considered critical or essential to the present invention unless explicitly indicated as being “critical” or “essential.”
-
FIG. 1 illustrates apump 10 of the invention having amotor 12 with ahousing 14 at one end and ahousing 16 at the other. Thehousings head assembly 18, which includeshead members tubes housings compression chamber portions housings housings pump 10 also includesfan guards 32, one at each end, which are essentially identical to one another. Thepump 10 of the present invention may be employed in a variety of applications, including but not limited to cable drying, sewage aeration, tire inflation, etc. - Referring to
FIGS. 2 and 3 , a partial cross section view of thepump 10 and an end view of thepump 10 with thefan guard 32 removed are shown, respectively. Themotor 12 has ashaft 34 which extends through it and into bothhousings respective housing housings housing 14 is shown inFIG. 2 . Each end of theshaft 34 mounts arotary fan blade 36 which is rotated by theshaft 34 within afan cavity 37 defined by thehousing 14 in a direction so as to draw air into eachrespective housing rotary fan blade 36 is secured to theshaft 34 using aspring clip 38. - The
housings ventilation slots 39 to allow the exhausting of cooling air. Thehousings mount bearings 40 which journal theshaft 34. Thehousings fan blade 36 reaches the coils of themotor 12. - The
pump 10 includes apiston assembly 42 including apiston cylinder 44 and apiston head 46 operating within thepiston cylinder 44 to compress the operating fluid (e.g., air) to provide the pumping action. Thepiston head 46 is coupled by a connectingrod 48 to an eccentric 50 fixed to theshaft 34. In operation, theshaft 34 and attached eccentric 50 rotates causing the connectingrod 48 andpiston head 46 to move within thepiston cylinder 44. A flapper valve (not shown) mounted to thevalve plate 52 allows the air to enter thepiston cylinder 44 on the downstroke of the piston cycle and seals to prevent air passage on the upstroke. Thepiston head 46 also includes apiston cup 54 constructed of Teflon® or other similar material that provides a sliding seal between thepiston head 46 and thepiston cylinder 44. Thepiston cup 54 has a service life that may vary based on the temperature of thepiston cylinder 44, with a higher cylinder temperature resulting in a shorter service life. - Besides allowing axial cooling air flow to dissipate heat that is transferred from the
motor 12 to thehousings bearings 40, thefan guard 32 also directs cooling flow over thepiston cylinder 44 to dissipate heat generated during the compression process. Thehousings FIG. 1 ) to allow the exhaust of cooling air directed over thepiston cylinder 44. - Turning now to
FIG. 4 an isometric back view of thefan guard 32 is provided. The front surface of thefan guard 32 is visible inFIG. 1 . Thefan guard 32 defines a cooling flow opening 57 in its front surface to provide for the passage of cooling flow past thefan guard 32. The fan guard includesrib members 58 spanning the cooling flow opening 57 andsupport members 60 running perpendicular to therib members 58. The spacing and arrangement of the rib andsupport members support members rotary fan blade 36. In the illustrated embodiment, thefan guard 32 is made of a resilient plastic resin, such as a polyester polymer. Thefan guard 32 includes atab 62 that interfaces with a corresponding notch 64 (shown inFIG. 2 ) in thehousing 14 to secure the bottom portion of thefan guard 32 to thehousing 16. Mountingholes 66 are defined in thefan guard 32 to allow the passage of screws for securing thefan guard 32 to thehousing 14 via corresponding holes 68 (shown inFIG. 3 ) in thehousing 14. Any means may be used to secure thefan guard 32 to thehousing 14. - The
fan guard 32 includes sidewalls 70 that define achannel 72. Thechannel 72 terminates in abaffle 74 that changes the direction of radial cooling flow generated by therotary fan blade 36 to impinge on thepiston cylinder 44, as indicated by thearrow 76 shown inFIG. 2 . Thesidewalls 70 also define a flaredportion 78 that collects the radial air flow and directs the flow into thechannel 72. - Returning to
FIG. 2 , therotary fan blade 36 includes anextended hub 80 that abuts the eccentric 50 to positively locate therotary fan blade 36 along theshaft 34 within thefan cavity 37. Therotary fan blade 36 is positioned to optimize the cooling provided to thepiston cylinder 44 by the cooling flow redirected by thefan guard 32. The optimal shaft position may be determined empirically and may vary depending on the particular geometry of thepump 10. In the illustrated embodiment, therotary fan blade 36 extends axially beyond thefan cavity 37 defined by thehousing 14 into the space bounded by thefan guard 32. This position has been found to increase the effectiveness of thefan guard 32 in redirecting the radial air flow to cool thepiston cylinder 44. - Redirecting cooling flow over the
piston cylinder 44, as described herein, reduces the operating temperature of thepiston assembly 42. The combination of therotary fan blade 36 andfan guard 32 also reduces the temperature of thebearings 40 and themotor 12. Such temperature reductions increase the operating lives of thepiston cup 54 and thebearings 40 for a given set of operating conditions. The improved heat dissipation characteristics may also be employed to extend the operating range of thepump 10 to allow operation at higher pressures, different voltages, and/or lower frequency voltage inputs. - The particular embodiments disclosed above are illustrative only, as the invention may be modified and practiced in different but equivalent manners apparent to those skilled in the art having the benefit of the teachings herein. Furthermore, no limitations are intended to the details of construction or design herein shown, other than as described in the claims below. It is therefore evident that the particular embodiments disclosed above may be altered or modified and all such variations are considered within the scope and spirit of the invention. Accordingly, the protection sought herein is as set forth in the claims below.
Claims (23)
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/986,752 US20060104833A1 (en) | 2004-11-12 | 2004-11-12 | Fan guard having channel to direct cooling air to a piston cylinder |
CA002523995A CA2523995A1 (en) | 2004-11-12 | 2005-10-19 | Fan guard having channel to direct cooling air to a piston cylinder |
EP05023696A EP1657440A1 (en) | 2004-11-12 | 2005-10-28 | Fan guard having channel to direct cooling air to a piston cylinder |
CN200510120180.8A CN1818380A (en) | 2004-11-12 | 2005-11-10 | Fan guard having channel to direct cooling air to a piston cylinder |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/986,752 US20060104833A1 (en) | 2004-11-12 | 2004-11-12 | Fan guard having channel to direct cooling air to a piston cylinder |
Publications (1)
Publication Number | Publication Date |
---|---|
US20060104833A1 true US20060104833A1 (en) | 2006-05-18 |
Family
ID=35432504
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/986,752 Abandoned US20060104833A1 (en) | 2004-11-12 | 2004-11-12 | Fan guard having channel to direct cooling air to a piston cylinder |
Country Status (4)
Country | Link |
---|---|
US (1) | US20060104833A1 (en) |
EP (1) | EP1657440A1 (en) |
CN (1) | CN1818380A (en) |
CA (1) | CA2523995A1 (en) |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20090148319A1 (en) * | 2007-12-05 | 2009-06-11 | Industrial Technology Research Institute | Linear compressor with permanent magnets |
US20130092252A1 (en) * | 2010-04-16 | 2013-04-18 | Loesomat Schraubtechnik Neef Gmbh | Housing for a hydraulic unit |
US8770341B2 (en) | 2011-09-13 | 2014-07-08 | Black & Decker Inc. | Compressor intake muffler and filter |
US8899378B2 (en) | 2011-09-13 | 2014-12-02 | Black & Decker Inc. | Compressor intake muffler and filter |
US20150001973A1 (en) * | 2012-02-08 | 2015-01-01 | Grundfos Holding A/S | Electric motor |
US20150316050A1 (en) * | 2014-04-30 | 2015-11-05 | Mat Industries, Llc | Compressor shroud having integral muffler and inertial filter |
CN112555119A (en) * | 2020-12-02 | 2021-03-26 | 东莞市莱诺机电科技有限公司 | Oil-free vacuum pump |
US11111913B2 (en) | 2015-10-07 | 2021-09-07 | Black & Decker Inc. | Oil lubricated compressor |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102014113598A1 (en) * | 2014-09-19 | 2016-03-24 | Knorr-Bremse Systeme für Schienenfahrzeuge GmbH | Multi-stage piston compressor with an external cooling air duct |
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US4186317A (en) * | 1976-10-07 | 1980-01-29 | Sisk Hollis D | Endplate with cast-in baffle |
US4190402A (en) * | 1975-05-06 | 1980-02-26 | International Telephone And Telegraph Corporation | Integrated high capacity compressor |
US4529365A (en) * | 1980-08-29 | 1985-07-16 | Durr-Dental Gmbh & Co., Kg | Compressor with longitudinally extending cooling fins |
US20040217661A1 (en) * | 2003-05-01 | 2004-11-04 | Frank Peter L. | Fan baffle |
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AU1930001A (en) * | 1999-11-29 | 2001-06-04 | Thomas Industries Inc. | Pump housing |
US6485266B2 (en) * | 2000-03-10 | 2002-11-26 | Thomas Industries, Inc. | Compressor assembly with deflector |
-
2004
- 2004-11-12 US US10/986,752 patent/US20060104833A1/en not_active Abandoned
-
2005
- 2005-10-19 CA CA002523995A patent/CA2523995A1/en not_active Abandoned
- 2005-10-28 EP EP05023696A patent/EP1657440A1/en not_active Withdrawn
- 2005-11-10 CN CN200510120180.8A patent/CN1818380A/en active Pending
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4190402A (en) * | 1975-05-06 | 1980-02-26 | International Telephone And Telegraph Corporation | Integrated high capacity compressor |
US4186317A (en) * | 1976-10-07 | 1980-01-29 | Sisk Hollis D | Endplate with cast-in baffle |
US4529365A (en) * | 1980-08-29 | 1985-07-16 | Durr-Dental Gmbh & Co., Kg | Compressor with longitudinally extending cooling fins |
US20040217661A1 (en) * | 2003-05-01 | 2004-11-04 | Frank Peter L. | Fan baffle |
Cited By (24)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20090148319A1 (en) * | 2007-12-05 | 2009-06-11 | Industrial Technology Research Institute | Linear compressor with permanent magnets |
US20130092252A1 (en) * | 2010-04-16 | 2013-04-18 | Loesomat Schraubtechnik Neef Gmbh | Housing for a hydraulic unit |
US9458845B2 (en) | 2011-09-13 | 2016-10-04 | Black & Decker Inc. | Air ducting shroud for cooling an air compressor pump and motor |
US8899378B2 (en) | 2011-09-13 | 2014-12-02 | Black & Decker Inc. | Compressor intake muffler and filter |
US20160298618A1 (en) * | 2011-09-13 | 2016-10-13 | Black & Decker Inc. | Compressor Intake Muffler And Filter |
US8770341B2 (en) | 2011-09-13 | 2014-07-08 | Black & Decker Inc. | Compressor intake muffler and filter |
US8967324B2 (en) | 2011-09-13 | 2015-03-03 | Black & Decker Inc. | Compressor housing having sound control chambers |
US9097246B2 (en) | 2011-09-13 | 2015-08-04 | Black & Decker Inc. | Tank dampening device |
US9127662B2 (en) | 2011-09-13 | 2015-09-08 | Black & Decker Inc. | Tank dampening device |
US10982664B2 (en) | 2011-09-13 | 2021-04-20 | Black & Decker Inc. | Compressor intake muffler and filter |
US9890774B2 (en) * | 2011-09-13 | 2018-02-13 | Black & Decker Inc. | Compressor intake muffler and filter |
US9309876B2 (en) | 2011-09-13 | 2016-04-12 | Black & Decker Inc. | Compressor intake muffler and filter |
US11788522B2 (en) | 2011-09-13 | 2023-10-17 | Black & Decker Inc. | Compressor intake muffler and filter |
US8851229B2 (en) | 2011-09-13 | 2014-10-07 | Black & Decker Inc. | Tank dampening device |
US9181938B2 (en) | 2011-09-13 | 2015-11-10 | Black & Decker Inc. | Tank dampening device |
US10012223B2 (en) | 2011-09-13 | 2018-07-03 | Black & Decker Inc. | Compressor housing having sound control chambers |
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US10871153B2 (en) | 2011-09-13 | 2020-12-22 | Black & Decker Inc. | Method of reducing air compressor noise |
US10243425B2 (en) * | 2012-02-08 | 2019-03-26 | Grundfos Holding A/S | Motor housing with electronic housing both having vertical partial cooling ribs for wet-running motor for a centrifugal pump |
US20150001973A1 (en) * | 2012-02-08 | 2015-01-01 | Grundfos Holding A/S | Electric motor |
US10436188B2 (en) * | 2014-04-30 | 2019-10-08 | Mat Industries, Llc | Compressor shroud having integral muffler and inertial filter |
US20150316050A1 (en) * | 2014-04-30 | 2015-11-05 | Mat Industries, Llc | Compressor shroud having integral muffler and inertial filter |
US11111913B2 (en) | 2015-10-07 | 2021-09-07 | Black & Decker Inc. | Oil lubricated compressor |
CN112555119A (en) * | 2020-12-02 | 2021-03-26 | 东莞市莱诺机电科技有限公司 | Oil-free vacuum pump |
Also Published As
Publication number | Publication date |
---|---|
CN1818380A (en) | 2006-08-16 |
EP1657440A1 (en) | 2006-05-17 |
CA2523995A1 (en) | 2006-05-12 |
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