US20050207905A1 - Fixed angle swash plate compressor - Google Patents
Fixed angle swash plate compressor Download PDFInfo
- Publication number
- US20050207905A1 US20050207905A1 US10/803,679 US80367904A US2005207905A1 US 20050207905 A1 US20050207905 A1 US 20050207905A1 US 80367904 A US80367904 A US 80367904A US 2005207905 A1 US2005207905 A1 US 2005207905A1
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- Prior art keywords
- swash plate
- bearing
- compressor
- shaft
- bearing assembly
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- 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.)
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- 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
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1054—Actuating elements
- F04B27/1063—Actuating-element bearing means or driving-axis bearing means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F42—AMMUNITION; BLASTING
- F42D—BLASTING
- F42D5/00—Safety arrangements
- F42D5/04—Rendering explosive charges harmless, e.g. destroying ammunition; Rendering detonation of explosive charges harmless
- F42D5/055—Silencing means for blasting operations
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- E—FIXED CONSTRUCTIONS
- E21—EARTH DRILLING; MINING
- E21D—SHAFTS; TUNNELS; GALLERIES; LARGE UNDERGROUND CHAMBERS
- E21D9/00—Tunnels or galleries, with or without linings; Methods or apparatus for making thereof; Layout of tunnels or galleries
- E21D9/006—Tunnels or galleries, with or without linings; Methods or apparatus for making thereof; Layout of tunnels or galleries by making use of blasting methods
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Rotary Pumps (AREA)
- Rolling Contact Bearings (AREA)
Abstract
A compressor is disclosed generally comprising a housing, a shaft disposed therein, and a swash plate part that is mounted at a fixed angle relative to the longitudinal axis of the shaft. In some embodiments, the swash plate part is coupled to a second, inner swash plate part via a bearing. In other embodiments, the swash plate part is coupled directly to the shaft via the bearing. The bearing is adapted to accommodate both the radial and axial loads of the compressor in order to eliminate the need for a separate thrust bearing.
Description
- The present invention relates to an apparatus for generating compressed fluid. More specifically, the invention relates to a swash plate compressor that maintains a fixed angle while minimizing the number of bearing assemblies required.
- Swash plate compressors are generally known in the art. These compressors typically employ a cylinder block with a plurality of piston channels mounted on a drive shaft. A plurality of pistons are slidably disposed in the piston channels and are coupled to a swash plate that is also mounted on the drive shaft. In accordance with the rotation of the drive shaft, the swash plate pivots, causing reciprocal motion of the pistons within the piston channels, thereby alternately creating suction and compression strokes.
- These compressors employ a variety of mechanisms that utilize the rotational force of the drive shaft to make the swash plate pivot, such as an actuating assembly with a slanted surface underneath the swash plate, as disclosed in U.S. Pat. No. 6,439,857 to Koelzer and assigned to the assignee of the present application, an assembly of rotating and non-rotating plates, as disclosed in U.S. Pat. No. 5,626,463 to Kimura, and a rotatable cylinder block, as disclosed in U.S. Pat. No. 5,394,698 to Takagi.
- As the swash plate pivots, the pistons reciprocate within the piston channels of the cylinder block, alternately drawing fluid to be compressed into the channels and subsequently compressing and discharging the fluid. In this way, the rotational force of the shaft is converted into axial motion of the pistons, enabling the pistons to alternately perform the functions of suction and compression, and thus, fluid is first drawn into a piston channel and is subsequently compressed and discharged from the piston channel.
- One problem with these swash plate compressors, however, is that they are typically difficult and expensive to manufacture, for several reasons. First, because the drive shaft on which the swash plate is mounted rotates, and because the swash plate is connected to pistons which are disposed in the piston channels in the cylinder block, the compressor typically requires a somewhat complex assembly to accommodate these competing interests of rotation and non-rotation. Even if an advantageous bearing assembly such as that disclosed in U.S. Pat. No. 6,439,857 to Koelzer is utilized, one must still employ an actuating mechanism as disclosed therein in order for the swash plate to function properly.
- Moreover, due to the nature and function of a compressor swash plate, the swash plate assembly necessarily experiences both radial and axial loads as a result of the simultaneous rotational motion of the swash plate and axial motion of the pistons. Accordingly, it is necessary for these assemblies to employ both radial bearings and thrust bearings, such as the design disclosed in U.S. Patent Application U.S. 2001/0008607 (Richter).
- What is desired, therefore, is a swash plate compressor that is inexpensive to manufacture. What is further desired is a swash plate compressor that is easy to assemble. What is also desired is a swash plate compressor that minimizes the amount of bearings required.
- Accordingly, it is an object of the present invention to provide a swash plate compressor that is not complex.
- It is a further object of the present invention to provide a swash plate compressor that does not require an actuating mechanism for the swash plate.
- It is yet another object of the present invention to provide a swash plate compressor that does not require separate radial and thrust bearings.
- In order to overcome the deficiencies of the prior art and to achieve at least some of the objects and advantages listed, the invention comprises a compressor including a housing, a shaft disposed in the housing, the shaft having a longitudinal axis, an inner swash plate portion attached to the shaft at a fixed angle relative to the longitudinal axis of the shaft, an outer swash plate portion coupled to the inner swash plate portion, and a bearing assembly by which the outer swash plate portion is coupled to the inner swash plate portion, wherein the bearing assembly is adapted to accommodate both the radial load and the axial load of the swash plate portions.
- In another embodiment, the invention comprises a compressor including a housing, a shaft disposed in the housing, the shaft having a longitudinal axis, a swash plate coupled to the shaft at a fixed angle relative to the longitudinal axis of the shaft, and a bearing assembly by which the swash plate is coupled to the shaft, wherein the bearing assembly is adapted to accommodate both the radial load and the axial load of the swash plate.
- In yet another embodiment, the invention comprises a compressor including a housing having at least one piston channel, a shaft disposed in the housing, a swash plate coupled to the shaft, at least one piston disposed in the at least one piston channel and movable therein, wherein the swash plate is coupled to the at least one piston and inclined at an angle relative to the direction of motion thereof, and a bearing assembly by which the swash plate is coupled to the shaft, such that the angle at which the swash plate is inclined relative to the direction of motion of the at least one piston remains fixed as the shaft rotates, wherein the bearing assembly is adapted to accommodate both the radial load and the axial load of the swash plate.
- In still another embodiment, the invention comprises a compressor including a housing, a shaft disposed in the housing, the shaft having a longitudinal axis, an inner swash plate portion attached to the shaft at a fixed angle relative to the longitudinal axis of the shaft, an outer swash plate portion coupled to the inner swash plate portion, and an angular contact bearing by which the outer swash plate portion is coupled to the inner swash plate portion.
- In yet another embodiment, the invention comprises a compressor including a housing, a shaft disposed in the housing, the shaft having a longitudinal axis, a swash plate coupled to the shaft at a fixed angle relative to the longitudinal axis of the shaft, and an angular contact bearing by which the swash plate is coupled to the shaft.
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FIG. 1 is an isometric view of a swash plate compressor in accordance with the invention. -
FIG. 2 is a cross-sectional side view of the compressor ofFIG. 1 . -
FIG. 3 is a cross-sectional side view of another embodiment of the compressor ofFIG. 1 . -
FIG. 4 is an isometric view of the swash plate assembly of the compressor ofFIG. 3 . -
FIG. 5 is another cut-away, cross-sectional side view of one embodiment of the shaft and swash plate of the compressor ofFIG. 1 . -
FIG. 6 a is a partial cross-sectional, isometric view of a standard radial bearing. -
FIG. 6 b is a partial cross-sectional, isometric view of an angular contact bearing of the swash plate of the compressor ofFIG. 1 . -
FIG. 7 is an exposed side view of the ball bearing ofFIG. 6 b. -
FIG. 8 is a partial cross-sectional, isometric view of a tapered roller bearing used in some embodiments of the swash plate of the compressor ofFIG. 1 . -
FIG. 9 is a cross-sectional side view of a four point contact bearing used in some embodiments of the swash plate of the compressor ofFIG. 1 . -
FIG. 10 a is a cross-sectional side view of a tandem duplex-bearing used in some embodiments of the swash plate of the compressor ofFIG. 1 . -
FIG. 10 b is a cross-sectional side view of a face-to-face duplex-bearing used in some embodiments of the swash plate of the compressor ofFIG. 1 . -
FIG. 10 c is a cross-sectional side view of a back-to-back duplex-bearing used in some embodiments of the swash plate of the compressor ofFIG. 1 . -
FIG. 10 d is a cross-sectional side view of a double row angular contact bearing used in some embodiments of the swash plate of the compressor ofFIG. 1 . -
FIG. 10 e is a cross-sectional side view of a shielded type of the double row angular contact bearing ofFIG. 10 d. -
FIG. 10 f is a cross-sectional side view of a sealed type of the double row angular contact bearing ofFIG. 10 d. - The basic components of one embodiment of a
swash plate compressor 10 in accordance with the invention are illustrated inFIG. 1 . As used in the description, the terms “top,” “bottom,” “above,” “below,” “over,” “under,” “on top,” “underneath,” “up,” “down,” “upper,” “lower,” “front,” “rear,” “forward” and “back” refer to the objects referenced when in the orientation illustrated in the drawings, which orientation is not necessary for achieving the objects of the invention. - Typically, the
compressor 10 includes amain body 12, arear mounting cover 14, and afront mounting flange 16. When in use, thecompressor 10 is installed on a vehicle, such as an over-the-road truck, and generates compressed air for the vehicle's pressure system, which typically includes a tank (not shown) that supplies the compressed air to various accessories, such as, for example, the brake system. This production of the compressed air begins by receiving air, which may or may not be delivered from a turbocharger (not shown), in response to a reduction of the air pressure in the air system to or below a reference pressure. Though, in the embodiment described herein, the fluid is air, in certain other embodiments, the fluid may comprises any of various gases, liquids, or mixtures thereof. - The basic components of one embodiment of the
main body 12 of thecompressor 10 are illustrated inFIG. 2 . Themain body 12 includes aswash plate housing 20 defining aswash plate chamber 22 therein, and astationary cylinder block 26 mounted to thehousing 20. Adrive shaft 40 extends through both thehousing 20 and thecylinder block 26 and is rotatable therein. Aswash plate 24 is disposed in theswash plate chamber 22 and mounted on theshaft 40. A plurality ofpistons 30 are coupled to theswash plate 24, and thecylinder block 26 has a plurality ofpiston channels 32 that receive thepistons 30. Thepistons 30 are reciprocally displaceable within thepiston channels 32 in order to produce suction and compression strokes. - Each
piston 30 has aface 31 for contacting the air to be compressed. Accordingly, acompression chamber 34 is formed from the space in thepiston channel 32 to which thepiston face 31 is exposed. Thecompression chamber 34, which is in fluid communication with the air system, both receives air to be compressed and discharges air after compressing it. Accordingly, the air pressure in thecompression chamber 34 corresponds to the air pressure in the air system, thereby ensuring a state of pressure equilibrium for thecompressor 10, as is further explained below. - Typically, the
main body 12 of thecompressor 10 further includes acompressor head 18 mounted adjacent to thecylinder block 26. The compressor head has aninlet channel 80 and anoutlet channel 82 that are both in communication with thecompression chambers 34. In order to regulate the entry of uncompressed air from theinlet channel 80, and the discharge of compressed air to theoutlet channel 82, and to prevent the back-feeding of this air, thecompressor 10 is typically provided with a plurality of inlet andoutlet valves valves compressor head 18, or are created usingvalve plates compressor head 18 and thecylinder block 26. - In some embodiments, the
compressor head 18 is provided with inlet and outlet ports, 90, 92, which are in fluid communication with the inlet andoutlet channels inlet port 90, into theinlet channel 80 and past theinlet valves 84, to thecompression chambers 34 where it can be compressed. Similarly, once air is compressed and discharged from thecompression chambers 34 through theoutlet valves 85 and into theoutlet channel 82, the air may be directed to the air system via theoutlet port 92. - In other embodiments, however, as shown in
FIG. 3 , theswash plate housing 20 is provided with aninlet port 91, thereby eliminating the need for an inlet port in thecompressor head 18. In these embodiments, air enters theswash plate chamber 22, cooling any bearings that may be found therein, and is communicated to theinlet channel 80 via apassageway 93. - In certain advantageous embodiments, as illustrated in
FIGS. 3-4 , theswash plate 24 has an outer part 42 andinner part 44, wherein the outer part 42 is coupled to theinner part 44 via a bearing 46. Theinner part 44 is mounted on theshaft 40 with a series ofpins 48, such that theinner part 44 rotates with theshaft 40. As theshaft 40 rotates, the bearing 46 permits the outer part 42 of theswash plate 24 to be restrained as theinner part 44 rotates with theshaft 40. Accordingly, the outer part 42, thepistons 30, and thecylinder block 26 can all be non-rotating. With this arrangement, theshaft 40 can continue to rotate even when thecompressor 10 is not compressing air and thepistons 30 are idle. As a consequence, accessories coupled to theshaft 40, such as, for example, a fuel pump (not shown), continue to function. - In certain embodiments, in order to prevent the outer part 42 from rotating, the
swash plate 24 receives aradially extending stopper 49 that engages an axial groove of thehousing 20, as shown inFIG. 4 . In other embodiments, as shown inFIG. 2 , agimbal arm 100 may be used to prevent the outer part 42 from rotating. - Refering again to
FIGS. 2-3 , in order to facilitate the reciprocal motion of thepistons 30 within thepiston channels 32, the entireswash plate 24 remains inclined at afixed angle 140 with respect to the longitudinal axis 39 of theshaft 40. Because theangle 140 is fixed, the inclined plane of theswash plate 24 rotates as theshaft 40 rotates. In this way, the rotational motion ofswash plate 24 about theshaft 40 causes reciprocal displacement of thepistons 30 parallel to the axis 39 of theshaft 40. - To permit this reciprocal displacement, the
pistons 30 are coupled to theswash plate 24 via a bearing. In the embodiment described herein, the outer part 42 of theswash plate 24 includes a plurality of ball links, each of which is comprised of aswash plate rod 52 and aball element 54. In certain embodiments, therods 52, which are typically spaced angularly equidistantly from one another along an outer periphery of theswash plate 24 and extend radially therefrom, are bolts having a thread on one end, which is screwed into theswash plate 24, and anut 58 on the opposite end. - The
ball element 54 has a spherical outer surface for slidably engaging aflange 62 of apiston rod 60, which extends parallel to therotating shaft 40. Accordingly, as the plane of inclination of theswash plate 24 rotates, and the position of theflange 62 changes relative to the plane perpendicular to the longitudinal axis 39 of thedrive shaft 40, the cooperating surfaces of theball element 54 andflange 62 slide relative to one another. Such relative displacement allows thepiston rod 60 andball element 54 to move axially together, while theball element 54 rotates within theflange 62 in response to the rotating angle of inclination of theswash plate 24. Though the cooperating surfaces of theball element 54 andflange 62 are depicted as annular, in certain embodiments, other shapes that move synchronously while being angularly displaced relative to one another may be used. Alternatively, in other embodiments, the bearing by which thepistons 30 are coupled to theswash plate 24 may take other forms. - As explained above, in certain advantageous embodiments, and outer swash plate part 42 is coupled to an inner
swash plate part 44 via a bearing 46, and the innerswash plate part 44, in turn, is attached to theshaft 40 at anangle 140 relative to the longitudinal axis 39 of theshaft 40 that remains fixed. Accordingly, while the bearing 46 enables the outer part 42 to not rotate along withinner part 44 andshaft 40, the angle of inclination of the outer part 42 will rotate along with the angle of inclination of theinner part 44. In this way, thepistons 30 are displaced back and forth within thepiston channels 32, thereby generating suction and compression strokes. - For example, the
inner part 44 may be connected to theshaft 40 by a plurality of fasteners, such aspins 48, such that theinner part 44 remains at a fixed angle with respect to the longitudinal axis 39 of theshaft 40. In other embodiments, theinner part 44 may be otherwise fixedly attached to theshaft 40, such as by welding theinner part 44 to theshaft 40, or by manufacturing theshaft 40 such that theinner part 44 is integrally formed therewith. - In other advantageous embodiments, as illustrated in
FIG. 5 , theswash plate 24 may consist of a single,non-rotating part 45 that is directly coupled to a shaft 41 in such a way that it does not rotate with the shaft 41. This may be accomplished, for example, by providing ashaft 40 having arace 43 integrally formed therein, and by employing a bearing assembly such as bearing 46. - In order to eliminate the need for a separate thrust bearing, the bearing 46 is a bearing adapted to accommodate not only the radial load resulting from the rotation of the
shaft 40 relative to at least a portion of theswash plate 24, but also the axial load resulting from the sliding motion of thepistons 30 within thepiston channels 32. In certain advantageous embodiments, this bearing comprises an angular contact bearing. As can be seen by comparingFIG. 6 a (which depicts a standard radial bearing) withFIG. 6 b (which depicts an angular contact bearing), an angular contact bearing, unlike a standard radial bearing, allows theball 110 to ride high on the edge of one of the raceways. - As illustrated in
FIGS. 6B-7 , this is accomplished by using raceways where one of theshoulders 112 is higher than theother shoulder 114, thehigher shoulder 112 of thefirst raceway 120 being located at the opposite end from thehigher shoulder 116 of the second raceway 122. As a result, instead of theball 110 contacting theraceway 120 at an angle directly perpendicular to the longitudinal axis 39 of theshaft 40, theball 110 will contact theraceway 120 at anangle 126, thereby enabling the bearing 46 to absorb more axial load. This angle ofcontact 126 is typically 15, 30, or 40 degrees from the normal angle of contact of a standard radial bearing, but does not necessarily have to be one of these specific angles. - In other embodiments, however, the bearing 46 may comprise any other bearing adapted to accommodate both the axial and radial loads of the
compressor 10. For example, as illustrated inFIG. 8 , the bearing 46 may comprise a tapered roller bearing. In other embodiments, where just a little more axial load accommodation is needed, a four point contact bearing, as shown inFIG. 9 , may be used. - In certain advantageous embodiments, the bearing assembly contains multiple angular contact bearings side by side, commonly referred to as a duplex bearing. For example, in some embodiments, the bearing assembly may comprise a tandem duplex bearing, as shown in
FIG. 10 a. In these embodiments, two angular contact bearings that are facing the same direction are positioned adjacent each other in order to increase the level of axial load that the bearing assembly is able to accommodate. - In other embodiments where the bearing assembly includes a duplex bearing—such as those where axial loads exist in two directions—two angular contact bearings may be positioned adjacent each other such the bearings are facing in opposite directions. These arrangements serve to offset opposing axial loads, and would be useful, for example, in double-acting or two-step piston compressors. In certain embodiments, as shown in
FIG. 10 b, a face-to-face duplex bearing is employed, which allows for a larger misalignment angle. In other embodiments, as shown inFIG. 10 c, a back-to-back duplex bearing is employed, which provides greater rigidity. - In some embodiments, a double row angular contact bearing is employed, as shown in
FIG. 10 d. In these embodiments, two rows of angular contact bearings are arranged with shoulders positioned similar to that of a back-to-back duplex bearing, but the inner andouter rings - In some of these embodiments, the bearings are shielded, as illustrated in
FIG. 10 e. In these bearings, shields 134, which, in some cases, are made of steel, are placed at either end of the bearing in order to keep foreign materials from entering the bearing. In other embodiments, the bearings are sealed, as illustrated inFIG. 10 f. In these embodiments, seals 136 are placed at either end of the bearing in order to both keep out foreign materials and keep in any grease that is used in the bearing. - It should be understood that the foregoing is illustrative and not limiting, and that obvious modifications may be made by those skilled in the art without departing from the spirit of the invention. Accordingly, reference should be made primarily to the accompanying claims, rather than the foregoing specification, to determine the scope of the invention.
Claims (26)
1. A compressor, comprising:
a housing;
a shaft disposed in said housing, said shaft having a longitudinal axis;
an inner swash plate portion attached to said shaft at a fixed angle relative to the longitudinal axis of said shaft;
an outer swash plate portion coupled to said inner swash plate portion; and
a bearing assembly by which said outer swash plate portion is coupled to said inner swash plate portion;
wherein said bearing assembly is adapted to accommodate both the radial load and the axial load of the swash plate portions.
2. The compressor as claimed in claim 1 , wherein said inner swash plate portion is integrally formed with said shaft.
3. The compressor as claimed in claim 1 , wherein said bearing assembly comprises an angular contact bearing.
4. The compressor as claimed in claim 3 , wherein said bearing assembly comprises a duplex bearing.
5. The compressor as claimed in claim 4 , wherein said bearing assembly comprises a tandem duplex bearing.
6. The compressor as claimed in claim 4 , wherein said bearing assembly comprises a back-to-back duplex bearing.
7. The compressor as claimed in claim 4 , wherein said bearing assembly comprises a face-to-face duplex bearing.
8. The compressor as claimed in claim 3 , wherein said bearing assembly comprises a double row angular contact bearing.
9. The compressor as claimed in claim 8 , wherein said bearing assembly is a shielded double row bearing.
10. The compressor as claimed in claim 8 , wherein said bearing assembly is a sealed double row bearing.
11. The compressor as claimed in claim 1 , wherein said bearing assembly comprises a four-point contact bearing.
12. The compressor as claimed in claim 1 , wherein said bearing assembly comprises a tapered roller bearing.
13. A compressor, comprising:
a housing;
a shaft disposed in said housing, said shaft having a longitudinal axis;
a swash plate coupled to said shaft at a fixed angle relative to the longitudinal axis of said shaft; and
a bearing assembly by which said swash plate is coupled to said shaft;
wherein said bearing assembly is adapted to accommodate both the radial load and the axial load of the swash plate.
14. The compressor as claimed in claim 13 , wherein said bearing assembly comprises an angular contact bearing.
15. The compressor as claimed in claim 14 , wherein said bearing assembly comprises a duplex bearing.
16. The compressor as claimed in claim 15 , wherein said bearing assembly comprises a tandem duplex bearing.
17. The compressor as claimed in claim 15 , wherein said bearing assembly comprises a back-to-back duplex bearing.
18. The compressor as claimed in claim 15 , wherein said bearing assembly comprises a face-to-face duplex bearing.
19. The compressor as claimed in claim 14 , wherein said bearing assembly comprises a double row angular contact bearing.
20. The compressor as claimed in claim 19 , wherein said bearing assembly is a shielded double row bearing.
21. The compressor as claimed in claim 19 , wherein said bearing assembly is a sealed double row bearing.
22. The compressor as claimed in claim 13 , wherein said bearing assembly comprises a four-point contact bearing.
23. The compressor as claimed in claim 13 , wherein said bearing assembly comprises a tapered roller bearing.
24. A compressor, comprising:
a housing having at least one piston channel;
a shaft disposed in said housing;
a swash plate coupled to said shaft;
at least one piston disposed in the at least one piston channel and movable therein;
wherein said swash plate is coupled to said at least one piston and inclined at an angle relative to the direction of motion thereof; and
a bearing assembly by which said swash plate is coupled to said shaft, such that the angle at which said swash plate is inclined relative to the direction of motion of the at least one piston remains fixed as said shaft rotates;
wherein said bearing assembly is adapted to accommodate both the radial load and the axial load of the swash plate.
25. A compressor, comprising:
a housing;
a shaft disposed in said housing, said shaft having a longitudinal axis;
an inner swash plate portion attached to said shaft at a fixed angle relative to the longitudinal axis of said shaft;
an outer swash plate portion coupled to said inner swash plate portion; and
an angular contact bearing by which said outer swash plate portion is coupled to said inner swash plate portion.
26. A compressor, comprising:
a housing;
a shaft disposed in said housing, said shaft having a longitudinal axis;
a swash plate coupled to said shaft at a fixed angle relative to the longitudinal axis of said shaft; and
an angular contact bearing by which said swash plate is coupled to said shaft.
Priority Applications (9)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/803,679 US20050207905A1 (en) | 2004-03-18 | 2004-03-18 | Fixed angle swash plate compressor |
MXPA05002989A MXPA05002989A (en) | 2004-03-18 | 2005-03-17 | Fixed angle swash plate compressor. |
AU2005201168A AU2005201168A1 (en) | 2004-03-18 | 2005-03-17 | Fixed angle swash plate compressor |
JP2005077410A JP2005264943A (en) | 2004-03-18 | 2005-03-17 | Swash plate type compressor with swash plate tilted at given angle |
CA002501150A CA2501150A1 (en) | 2004-03-18 | 2005-03-17 | Fixed angle swash plate compressor |
KR1020050022338A KR20060043772A (en) | 2004-03-18 | 2005-03-17 | Fixed angle swash plate compressor |
BR0500899-9A BRPI0500899A (en) | 2004-03-18 | 2005-03-18 | Fixed Angle Oscillating Plate Compressor |
EP05005939A EP1577552A3 (en) | 2004-03-18 | 2005-03-18 | Fixed angle swash plate compressor |
CNA2005100656276A CN1670370A (en) | 2004-03-18 | 2005-03-18 | Fixed angle swash plate compressor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/803,679 US20050207905A1 (en) | 2004-03-18 | 2004-03-18 | Fixed angle swash plate compressor |
Publications (1)
Publication Number | Publication Date |
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US20050207905A1 true US20050207905A1 (en) | 2005-09-22 |
Family
ID=34838924
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US10/803,679 Abandoned US20050207905A1 (en) | 2004-03-18 | 2004-03-18 | Fixed angle swash plate compressor |
Country Status (9)
Country | Link |
---|---|
US (1) | US20050207905A1 (en) |
EP (1) | EP1577552A3 (en) |
JP (1) | JP2005264943A (en) |
KR (1) | KR20060043772A (en) |
CN (1) | CN1670370A (en) |
AU (1) | AU2005201168A1 (en) |
BR (1) | BRPI0500899A (en) |
CA (1) | CA2501150A1 (en) |
MX (1) | MXPA05002989A (en) |
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US20090232667A1 (en) * | 2006-07-12 | 2009-09-17 | Hugelman Rodney D | Axial compressor |
US20130195691A1 (en) * | 2010-11-03 | 2013-08-01 | Dalei Liu | Swing Barrel Type Positive Displacement Pump Using Cross Shaft Joint Bearing |
US10094364B2 (en) | 2015-03-24 | 2018-10-09 | Ocean Pacific Technologies | Banded ceramic valve and/or port plate |
US20180290519A1 (en) * | 2017-04-05 | 2018-10-11 | Hyundai Motor Company | Air conditioner, vehicle including the same, and method for controlling the air conditioner |
US10309380B2 (en) | 2011-11-16 | 2019-06-04 | Ocean Pacific Technologies | Rotary axial piston pump |
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DE102004061235A1 (en) * | 2004-12-20 | 2006-07-06 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Dry-running swash plate compressor with a roller bearing swashplate |
CN101776055B (en) * | 2009-01-13 | 2012-05-23 | 刘大磊 | Drum-type displacement pump |
DE102014221778A1 (en) * | 2014-10-27 | 2016-04-28 | Robert Bosch Gmbh | transmission module |
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2005
- 2005-03-17 KR KR1020050022338A patent/KR20060043772A/en active Search and Examination
- 2005-03-17 AU AU2005201168A patent/AU2005201168A1/en not_active Abandoned
- 2005-03-17 CA CA002501150A patent/CA2501150A1/en not_active Abandoned
- 2005-03-17 MX MXPA05002989A patent/MXPA05002989A/en not_active Application Discontinuation
- 2005-03-17 JP JP2005077410A patent/JP2005264943A/en active Pending
- 2005-03-18 CN CNA2005100656276A patent/CN1670370A/en active Pending
- 2005-03-18 BR BR0500899-9A patent/BRPI0500899A/en not_active IP Right Cessation
- 2005-03-18 EP EP05005939A patent/EP1577552A3/en not_active Withdrawn
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Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20090232667A1 (en) * | 2006-07-12 | 2009-09-17 | Hugelman Rodney D | Axial compressor |
US20130195691A1 (en) * | 2010-11-03 | 2013-08-01 | Dalei Liu | Swing Barrel Type Positive Displacement Pump Using Cross Shaft Joint Bearing |
US9115712B2 (en) * | 2010-11-03 | 2015-08-25 | Dalei Liu | Swing barrel type positive displacement pump using cross shaft joint bearing |
US10309380B2 (en) | 2011-11-16 | 2019-06-04 | Ocean Pacific Technologies | Rotary axial piston pump |
US10094364B2 (en) | 2015-03-24 | 2018-10-09 | Ocean Pacific Technologies | Banded ceramic valve and/or port plate |
US20180290519A1 (en) * | 2017-04-05 | 2018-10-11 | Hyundai Motor Company | Air conditioner, vehicle including the same, and method for controlling the air conditioner |
CN108688440A (en) * | 2017-04-05 | 2018-10-23 | 现代自动车株式会社 | The vehicle of air-conditioning including the air-conditioning and the method for controlling the air-conditioning |
US10464396B2 (en) * | 2017-04-05 | 2019-11-05 | Hyundai Motor Company | Air conditioner, vehicle including the same, and method for controlling the air conditioner |
Also Published As
Publication number | Publication date |
---|---|
CA2501150A1 (en) | 2005-09-18 |
MXPA05002989A (en) | 2005-09-21 |
JP2005264943A (en) | 2005-09-29 |
BRPI0500899A (en) | 2005-11-01 |
AU2005201168A1 (en) | 2005-10-06 |
CN1670370A (en) | 2005-09-21 |
EP1577552A2 (en) | 2005-09-21 |
EP1577552A3 (en) | 2006-12-13 |
KR20060043772A (en) | 2006-05-15 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: HALDEX BRAKE CORPORATION, MISSOURI Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:KOELZER, ROBERT L.;JENKINS, MICHAEL R.;REEL/FRAME:015120/0441 Effective date: 20040302 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |