US3456874A - Cam driven compressor - Google Patents
Cam driven compressor Download PDFInfo
- Publication number
- US3456874A US3456874A US657651A US3456874DA US3456874A US 3456874 A US3456874 A US 3456874A US 657651 A US657651 A US 657651A US 3456874D A US3456874D A US 3456874DA US 3456874 A US3456874 A US 3456874A
- Authority
- US
- United States
- Prior art keywords
- cam
- compressor
- piston
- sliding block
- bearing
- 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.)
- Expired - Lifetime
Links
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
- F04B39/02—Lubrication
- F04B39/0223—Lubrication characterised by the compressor type
- F04B39/023—Hermetic compressors
- F04B39/0261—Hermetic compressors with an auxiliary oil pump
-
- 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
- F04B27/02—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders arranged oppositely relative to main shaft
-
- 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
- F04B39/10—Adaptations or arrangements of distribution members
- F04B39/1073—Adaptations or arrangements of distribution members the members being reed valves
Definitions
- This invention relates to a novel cam driven compressor generally, and more specifically, to a cam driven compressor having novel bearing lubrication means to permit high speed operation.
- a highly improved lubrication system is provided together with a novel lubrication means at the bearing surfaces of the compressor to allow sustained high speed operation of the compressor of the present case.
- the novel bearing arrangement and lubrication means also serves to allow high speed operation of the compressor of the instant case at relatively low noise levels.
- FIGURE 1 is a cross sectional view of a cam driven compressor showing certain elements and features of this invention.
- FIGURE 2 is a transverse sectional view of the compressor shown in FIGURE 1 taken along the section line 22.
- FIGURE 3 is a partial sectional view of the compressor taken along the section line 33 of FIGURE 1 illustrating further aspects of this invention.
- FIGURE 4 is a partial sectional view of the compressor taken along the section line 44 of FIGURE 2 and illustrating still further details and aspects of this invention.
- FIGURE 5 is a plan view taken along the lines 55 of FIGURE 2 showing the inlet and exhaust valve and port arrangement of the compressor of the instant invention.
- FIGURE 6 is a plan view taken along the section line 6-6 of FIGURE 2 illustrating further details of the exhaust valve.
- FIGURE 7 is a plan view taken along the section line 7-7 of FIGURE 2 illustrating in greater detail the inlet valve of the compressor of the present invention.
- FIGURE 8 is a plan view taken along the line 88 of FIGURE 2 and illustrating further aspects of the inlet and exhaust valves of the present invention.
- FIGURE 9 is a plan view of the cam block taken along the line 9 of FIGURE 2 and illustrating in detail an important feature of the present invention.
- FIGURE 10 is a lubrication pumping mechanism used in the present invention.
- FIGURE 11 is an overall view of the compressor of the present invention and illustrating further aspects of the present invention.
- FIGURES 1-11 DESCRIPTION OF THE PREFERRED EMBODIMENT Shown in FIGURES 1-11 is a typical compressor providing an environmental background in which the present invention is operable. Such compressor is designated generally by reference numeral 20.
- An important component of the compressor is a generally rectangular primary housing 22 having a cylindrical bore 24 therethrough.
- the primary housing 22 is closed at each of the axial ends by first and second head members 26 and 28 and first and second end caps 30 and 32.
- first and second bearing support members 34 and 36 Located adjacent either side of the compressor housing 22 are first and second bearing support members 34 and 36.
- Attached to the first bearing support member 34 is a cover plate 38.
- first and second head members 26 and 28 are located against the primary housing 22 and sandwiched by the first and second end caps 30 and 32.
- the head members 26 and 28 and the end caps 3t) and 32 are secured to the primary housing 22 by a plurality of removable fasteners 40.
- the first and second head members 26 and 28 cooperate with the primary housing 22 and a double acting piston member 42 to define a pair of air compression chambers 44 and 46 within the cylindrical bore 24 of the primary housing 22.
- the first and second end caps 30 and 32 are provided with a plurality of inlet ports 48 and exhaust ports 50. Flow through the inlet ports 48 is controlled by inlet valves 52.
- the inlet valves 52 are generally strip shaped spring material and extend across the cylindrical bore 24 of the compressor housing 22.
- the inlet valves 52 are pinned at one end portion 53 to the head members 26 and 28, by inlet valve dowels 54.
- Another end portion 56 of the inlet valves 52 is located within a recess 58 in the housing 22.
- the recess 58 serves to limit the travel of the intake valve 52 and further serves as a support for the spring action of the intake valves 52.
- exhaust valves 60 which cover the exhaust ports 50. As shown in FIGURES 5, 6 and 8, the exhaust valves 60 are located over the exhaust ports and are mounted on the head members 26 and 28 by dowel pins 62 located intermediate the ends of the exhaust valve 60. Also mounted on the head members 26 and 28 by means of the dowel pin 62 are exhaust valve backup members 64 which limit the travel of the exhaust valve 60 in an opening direction.
- the end caps 30 and 32 have a transverse web 66 which cooperates with the head members 26 and 28 to define an inlet passage 68 and an exhaust passage 70.
- the inlet passage 68 formed by the end caps 30 and 32 is connected wit-h a passageway 72 in the primary housing 22 and with the atmosphere by means of inlet port 74.
- the inlet port 74 and exhaust port 78 are surrounded by generally oval land portions 80 and 82 for the connection of appropriate fluid supply and delivery fittings, not shown. Because of the continuous nature of the inlet and exhaust passages, it is possible, as shown in FIGURE 11, that the inlet and exhaust lands 80 and 82 be located in various positions on the compressor such as at 80', 82. The optional location of the lands 80 and 82 allows a considerable amount of freedom in the application of the compressor of the present invention.
- the compressing piston 42 Located within the bore 24 of the primary housing 22 is the compressing piston 42.
- the piston 42 is double acting and is driven in a reciprocating manner through a cam block 84.
- the cam block 84 is driven by an eccentrically mounted circular cam 86 mounted on a cam shaft 88 which is driven by any suitable rotating power source such as an internal combustion engine.
- Thecam shaft 88 extends through the primary compressor housing 22 and into the second bearing support member 36 where the cam shaft 88 is supported in a bearing 92. Adjacent a journal 90 on the cam shaft 88 is a counterweight 94. Also located within the primary cornpressor housing 22 is a second counterweight 96 which is removably secured to the cam shaft 88 to allow easy assembly of the cam shaft with the remainder of the compressor. The second counterweight 96 is removably secured to the cam shaft 88 by means of fasteners 98. A ball bearing 100 is mounted in the first bearing support member 34 and supports the cam shaft 88 for rotation.
- bushing 102 and seal 104 are located on the cam shaft 88 and prevent the leakage of lubrieating fluid and the entry of dirt to the bearing 100.
- the pump assembly 106 Connected to the cam shaft 88 and supported by the second bearing support member 36 is a pump assembly 106 for supplying lubricating fluid to the various bearing elements of the compressor.
- the pump assembly 106 comprises a rotor member 108 mounted on a snout portion 110 of the cam shaft 88.
- a freely rotatable driven member 114 Located within an eccentric bore 112 of the second bearing support member 36 is a freely rotatable driven member 114.
- the pump assembly with the above identified elements comprises a pumping arrangement commonly known in the art as a Gerotor pump.
- Also provided in the second bearing support member 36 is a lubrication intake passage 116 and an exhaust passage 118.
- the inlet passage 116 is connected to a sump 120 by a conduit 122.
- the exhaust passage 118 is connected by internal ducting to a port 125 located adjacent the snout portion 110 of the cam shaft 88.
- the cam shaft 88 contains a bore 124 for the delivery of lubricating oil to the ball bearing 100 and to the slid- I ing block 84 by means of a secondary bore 126.
- the sliding block 84 is provided with oil delivery passages 128 for the delivery of oil from the lubricating pump assembly 106 to the bearing surface between the cam block 84 and the piston 42.
- the cam block 84 as shown in FIGURE 9 is provided with lubricating grooves 130 on the bearing surfaces 132 thereof.
- FIGURES 1 through 11 for a more specific discussion and description of the various elements and their functions in the compressor.
- the cam shaft 88 is adapted to be rotatably driven within the compressor housing 22 by an external power source not shown. As can be seen from FIGURE 1, the cam shaft 88 will rotate about an axis defined by the ball bearing 100 mounted in the cover plate 34 and the journal bearing 92 located in the second cover plate 36. Located intermediate the ball bearing 100 and the journal bearing 92 and as indicated above, is a circular cam element 86 which is mounted eccentric of the axis of rotation of the cam shaft 88. As can be better seen in FIGURE 2, located concentric with the circular cam element 86 is a sliding cam block 84 adapted to be driven by the cam element 86.
- rotation of the cam shaft 88 may, of course, be in either direction, but for purposes of illustration and description, rotation of the cam shaft 88 in the direction of the arrow in FIG- URE 2 has been assumed.
- Rotation of the cam shaft 88 from the position shown in FIGURE 2 will cause the cam block 84 to move upwardly and to the right and moving the piston 42 therewith.
- the maximum displacement of the piston 42 is governed by the dimension of eccentricity 2 shown in FIGURE 2 of the drawings.
- the maximum displacement of the piston 42 is twice the eccentricity e of the cam element 86. Further rotation of the shaft 88 from the vertical position of the axis of eccentricity of the cam element 86 will cause the piston element 42 to begin its downward movement. Since the inlet 'valve 52 and the exhaust valve 60 normally maintain the compression chambers 44 and 46 in an air tight condition, the downward movement of the piston 42 will cause a partial vacuum to exist in the compression chamber 44. Since the inlet ports 48 are open to the atmosphere through the passages 68 and 72 through the inlet port 74, the inlet valves 52 mounted on the head member 26 will be forced open by the pressure differential existing in the passageway 68 and the air compression chamber 44.
- a sump 120 is provided in the primary compressor housing 22 to receive a quantity of lubricating fluid.
- Extending from the second bearing support member 36 to the sump 120 is a conduit member 122 which is provided to allow the flow of lubricating fluid from the sump to the inlet passage 116 in the bearing support member 36.
- the lubrication inlet passage 116 is in communication with the inlet side of a pumping mechanism 106 shown in FIG- URE of the drawing.
- the pumping mechanism 106 comprises a rotor element 108 which is non-rotatably secured to the snout portion 110 of the cam shaft 88 and a rotatable element 114 I which is eccentrically located in the bearing support member 36 with respect to the axis of rotation of the cam shaft 88.
- the operation of a pump mechanism of this type is generally understood to those skilled in the art.
- the outer pumping element 114 is provided with more teeth than the rotor element 108. As the rotor element 108 is caused to rotate by the cam shaft 88, the outer pumping element 114 rotates in the same direction as the rotor element 108 at a speed related to the difference in the number of teeth between the outer pumping element 114 and the rotor element 108. The relative rotation of the rotor element 108 and the outer pumping element 114 provides a pumping action.
- the pumping action of the pumping mechanism 106 is used to supply pressurized lubricating fluid to the chamber 125 in the bearing support member 36. From the' chamber 125 the lubricating fluid is forced through the bores 124, 126 and 127 in the cam shaft 88 for the purposes of lubricating the ball bearing 100 and the bearing surface existing between the eccentric cam 86 and the sliding block 84.
- the journal 90 and the bearing 92 in the bearing support member 36 are lubricated by leakage of the pump assembly 106.
- the lubricating fluid As the lubricating fluid is forced through the bore 124 in the cam shaft 88 by the pumping means 106 the fluid flows radially outwardly from the bore 124 through a secondary lubrication passage 126 in the eccentric cam member 86. From the bore 126 in the cam shaft 88 the lubricating fluid flows in to the circumferential channel 136 in the sliding block member 84.
- This channel of pressurized lubricating fluid between the cam element 86 and the sliding block 84 provides for pressurized lubrication between the cam element 86 and the sliding block 84 along the bearing surface 138.
- the lubricating channel 136 is also in communication with a pair of lubricating bores 128 in the sliding block member 84.
- the bores 128 communicate with a pair of diagonal grooves 130 on the bearing surfaces 132 of the sliding block 84.
- Oil under pressure flows from the lubricating channel 136 through the bores 128 and into the diagonal grooves 130 of the sliding block member 84.
- the pressurized fluid attempts to lift the bearing surface 132 of sliding block from the bearing surfaces 134 of the piston member 42.
- a lubricating fluid film which prevents contact of the sliding block member 84 with the bearing surface 134 of the piston member 42. Since there is no contact existing between the' sliding block 84 and the bearing surface 134 of piston 42 it is readily apparent that there is a substantial reduction in friction existing therebetween.
- the lubricating fluid Once the lubricating fluid has served the purpose of lubricating the various bearing elements 100, 92 and the bearing surfaces existing between the cam element 86 and the sliding block 84 and between the sliding block 84 and the bearing surface 134 of the piston member 42, the lubricating fluid returns in a generally random manner to the sump of the primary compressor housing 22.
- the sliding block 84 and the piston 42 must be constructed of materials having substantially similar coefficients of expansion in order to prevent the sliding block 84 and the piston 42 from having in the alternative, excessive clearance or insuflicient clearance at normal operating temperatures of the compressor, once an initial satisfactory clearance has been established.
- Excessive clearance results in a breakdown of the hydrostatic bearing surface by preventing proper pressurization of the lubricating fluid and further results in excessive noise during operation.
- Insuflicient clearance likewise results in improper compressor operation by preventing the proper formation of a hydrostatic bearing surface and thereby results in increased friction and wear between the sliding block 84 and the piston 42.
- the removable counterweight 96 facilitates the easy assembly of the sliding block member 84 and the piston member 42 on the eccentric cam portion 86 of the cam shaft 88. Further, the removable counterweight 96 facilitates the easy assembly of the cam shaft with the remainder of the compressor by allowing assembly of the compressor through the opening covered by bearing support member 34.
- a compressor for pressurizing fluid comprising:
- a housing having a bore therein and defining a plurality of fluid flow passages
- a piston reciprocally mounted in said bore and cooperating with the housing to define a compression chamber
- a sliding block member operatively connected with the piston in sliding, driving relationship therewith, said operative connection including a predetermined flow restrictive clearance between the piston and the block and the sliding block member further having a circular bore therethrough;
- cam shaft assembly mounted on the housing and including a circular cam element eccentrically attached thereto, said cam element being located concentrically with the sliding block member and in driving relationship therewith;
- a pump assembly mounted on the housing and driven by the cam shaft for supplying a quantity of pressurized fluid to the flow restrictive clearance between the piston and the sliding block member and between the sliding block member and the circular cam element,
- the piston and the sliding block member are constructed of materials having substantially the same coefficient of thermal expansion.
- piston and sliding block member are constructed of materials having substantially the same coeflicients of thermal expansion.
- the sliding block member having a circumferential groove in the bore thereof in communication with the source of pressurized lubricating fluid; and wherein the sliding block member and the cam element cooperate to define a flow restrictive clearance therewhereby a fluid load bearing film is maintained between the sliding block member and the cam element.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Description
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US65765167A | 1967-08-01 | 1967-08-01 |
Publications (1)
Publication Number | Publication Date |
---|---|
US3456874A true US3456874A (en) | 1969-07-22 |
Family
ID=24638076
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US657651A Expired - Lifetime US3456874A (en) | 1967-08-01 | 1967-08-01 | Cam driven compressor |
Country Status (4)
Country | Link |
---|---|
US (1) | US3456874A (en) |
BR (1) | BR6800564D0 (en) |
FR (1) | FR1583281A (en) |
GB (1) | GB1183774A (en) |
Cited By (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3685923A (en) * | 1970-11-06 | 1972-08-22 | Gen Motors Corp | Automotive air conditioning compressor |
US3784331A (en) * | 1972-05-18 | 1974-01-08 | Gen Motors Corp | Radial compressor with two-piece cylinder housing and shell |
US3806284A (en) * | 1973-03-08 | 1974-04-23 | Gen Motors Corp | Compressor with counterweight means |
US3871793A (en) * | 1973-12-28 | 1975-03-18 | Jr John W Olson | Automotive refrigeration compressor module |
US3878768A (en) * | 1971-07-24 | 1975-04-22 | Herwig Kress | Hydrostatic transmission |
JPS5156610U (en) * | 1974-10-30 | 1976-05-04 | ||
US4072210A (en) * | 1976-01-19 | 1978-02-07 | Chien Chao C | Compressor |
US4132510A (en) * | 1976-06-09 | 1979-01-02 | Sampei Komiya | Compressor |
US4373876A (en) * | 1980-03-21 | 1983-02-15 | Musashi Seimitsu Kogyo Kabushiki Kaisha | Double-acting piston compressor |
US4396363A (en) * | 1980-09-16 | 1983-08-02 | Nippon Piston Ring Co., Ltd. | Small reciprocating pump |
US4518323A (en) * | 1983-07-25 | 1985-05-21 | Copeland Corporation | Hermetic refrigeration compressor |
US5556267A (en) * | 1993-02-05 | 1996-09-17 | Hansen Engine Corporation | Double acting pump |
WO2005003558A1 (en) * | 2003-07-07 | 2005-01-13 | Bernhard Frey | Eccentric drive mechanism for volumetric pumps or motors |
US20060275164A1 (en) * | 2003-02-11 | 2006-12-07 | Marco Ganser | High pressure pump |
US20190093647A1 (en) * | 2017-09-28 | 2019-03-28 | Lg Electronics Inc. | Lubricating oil supply apparatus and compressor using lubricating oil supply apparatus |
US11022116B2 (en) * | 2018-01-19 | 2021-06-01 | Lg Electronics Inc. | Lubricant supply device and a compressor using the same |
US20230204022A1 (en) * | 2021-12-29 | 2023-06-29 | Transportation Ip Holdings, Llc | Air compressor system |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1631425A (en) * | 1923-03-01 | 1927-06-07 | Henry C Marcus | Compressor |
US1652565A (en) * | 1927-12-13 | Pttmcp | ||
US1696673A (en) * | 1925-10-08 | 1928-12-25 | Fourness Dev Corp | Compressor |
US2751145A (en) * | 1952-10-21 | 1956-06-19 | Gen Motors Corp | Refrigerating apparatus |
US2993641A (en) * | 1958-07-25 | 1961-07-25 | Roy T Chew | Compressor lubrication system |
US3211365A (en) * | 1961-10-16 | 1965-10-12 | Copeland Refrigeration Corp | Compressor structure |
US3307480A (en) * | 1964-09-01 | 1967-03-07 | Carrier Corp | Automatically reversible gear pump |
-
1967
- 1967-08-01 US US657651A patent/US3456874A/en not_active Expired - Lifetime
-
1968
- 1968-06-12 GB GB27942/68A patent/GB1183774A/en not_active Expired
- 1968-07-11 BR BR200564/68A patent/BR6800564D0/en unknown
- 1968-07-23 FR FR1583281D patent/FR1583281A/fr not_active Expired
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1652565A (en) * | 1927-12-13 | Pttmcp | ||
US1631425A (en) * | 1923-03-01 | 1927-06-07 | Henry C Marcus | Compressor |
US1696673A (en) * | 1925-10-08 | 1928-12-25 | Fourness Dev Corp | Compressor |
US2751145A (en) * | 1952-10-21 | 1956-06-19 | Gen Motors Corp | Refrigerating apparatus |
US2993641A (en) * | 1958-07-25 | 1961-07-25 | Roy T Chew | Compressor lubrication system |
US3211365A (en) * | 1961-10-16 | 1965-10-12 | Copeland Refrigeration Corp | Compressor structure |
US3307480A (en) * | 1964-09-01 | 1967-03-07 | Carrier Corp | Automatically reversible gear pump |
Cited By (23)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3685923A (en) * | 1970-11-06 | 1972-08-22 | Gen Motors Corp | Automotive air conditioning compressor |
US3878768A (en) * | 1971-07-24 | 1975-04-22 | Herwig Kress | Hydrostatic transmission |
US3784331A (en) * | 1972-05-18 | 1974-01-08 | Gen Motors Corp | Radial compressor with two-piece cylinder housing and shell |
US3806284A (en) * | 1973-03-08 | 1974-04-23 | Gen Motors Corp | Compressor with counterweight means |
US3871793A (en) * | 1973-12-28 | 1975-03-18 | Jr John W Olson | Automotive refrigeration compressor module |
JPS5156610U (en) * | 1974-10-30 | 1976-05-04 | ||
JPS5444247Y2 (en) * | 1974-10-30 | 1979-12-19 | ||
US4072210A (en) * | 1976-01-19 | 1978-02-07 | Chien Chao C | Compressor |
US4132510A (en) * | 1976-06-09 | 1979-01-02 | Sampei Komiya | Compressor |
US4373876A (en) * | 1980-03-21 | 1983-02-15 | Musashi Seimitsu Kogyo Kabushiki Kaisha | Double-acting piston compressor |
US4396363A (en) * | 1980-09-16 | 1983-08-02 | Nippon Piston Ring Co., Ltd. | Small reciprocating pump |
US4518323A (en) * | 1983-07-25 | 1985-05-21 | Copeland Corporation | Hermetic refrigeration compressor |
US5556267A (en) * | 1993-02-05 | 1996-09-17 | Hansen Engine Corporation | Double acting pump |
US20060275164A1 (en) * | 2003-02-11 | 2006-12-07 | Marco Ganser | High pressure pump |
WO2005003558A1 (en) * | 2003-07-07 | 2005-01-13 | Bernhard Frey | Eccentric drive mechanism for volumetric pumps or motors |
US7441492B2 (en) | 2003-07-07 | 2008-10-28 | Bernhard Frey | Eccentric drive mechanism for volumetric pumps or motors |
CN1846058B (en) * | 2003-07-07 | 2010-04-21 | 贝恩哈尔·弗雷 | Eccentric drive mechanism for volumetric unidirectional pumps |
NO338172B1 (en) * | 2003-07-07 | 2016-08-01 | Frey Bemhard | Eccentric drive mechanism for volumetric pumps and motors |
US20190093647A1 (en) * | 2017-09-28 | 2019-03-28 | Lg Electronics Inc. | Lubricating oil supply apparatus and compressor using lubricating oil supply apparatus |
US11242846B2 (en) * | 2017-09-28 | 2022-02-08 | Lg Electronics Inc. | Lubricating oil supply apparatus and compressor using lubricating oil supply apparatus |
US11022116B2 (en) * | 2018-01-19 | 2021-06-01 | Lg Electronics Inc. | Lubricant supply device and a compressor using the same |
US20230204022A1 (en) * | 2021-12-29 | 2023-06-29 | Transportation Ip Holdings, Llc | Air compressor system |
US11913441B2 (en) * | 2021-12-29 | 2024-02-27 | Transportation Ip Holdings, Llc | Air compressor system having a hollow piston forming an interior space and a check valve in a piston crown allowing air to exit the interior space |
Also Published As
Publication number | Publication date |
---|---|
FR1583281A (en) | 1969-10-24 |
GB1183774A (en) | 1970-03-11 |
BR6800564D0 (en) | 1973-01-02 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: SIGNET SYSTEMS, INC., HARRODSBURG, KY., Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:EATON CORPORATION;REEL/FRAME:004162/0483 Effective date: 19830630 Owner name: BA COMMERCIAL CORPORATION, 1621 CEDAR CREST BLVD., Free format text: SECURITY INTEREST;ASSIGNOR:SIGNET SYSTEMS, INC.;REEL/FRAME:004162/0476 Effective date: 19830630 |
|
AS | Assignment |
Owner name: BA COMMERCIAL CORPORATION, 1621 CEDAR CREST BLVD., Free format text: SECURITY INTEREST;ASSIGNOR:SIGNET SYSTEMS, INC.;REEL/FRAME:004219/0216 Effective date: 19830630 |
|
AS | Assignment |
Owner name: CONNECTICUT BANK AND TRUST COMPANY, N.A. THE, 900 Free format text: SECURITY INTEREST;ASSIGNOR:SIGNET SYSTEMS, INC.;REEL/FRAME:004302/0861 Effective date: 19840906 Owner name: SIGNET SYSTEMS, INC., TAPP ROAD, P.O. BOX 367 HARR Free format text: RELEASED BY SECURED PARTY;ASSIGNOR:BANCAMERICA COMMERCIAL CORPORATION;REEL/FRAME:004302/0856 Effective date: 19840809 |
|
AS | Assignment |
Owner name: SIGNET SYSTEMS, INC.,CALIFORNIA Free format text: RELEASED BY SECURED PARTY;ASSIGNOR:CONNECTICUT BANK AND TRUST COMPANY, N.A., THE;REEL/FRAME:004907/0216 Effective date: 19861024 Owner name: SIGNET SYSTEMS, INC., 1531 POMONA RD., CORONA, CA Free format text: RELEASED BY SECURED PARTY;ASSIGNOR:CONNECTICUT BANK AND TRUST COMPANY, N.A., THE;REEL/FRAME:004907/0216 Effective date: 19861024 |