US3788780A - Intake-valve-free compressor - Google Patents

Intake-valve-free compressor Download PDF

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Publication number
US3788780A
US3788780A US00269776A US3788780DA US3788780A US 3788780 A US3788780 A US 3788780A US 00269776 A US00269776 A US 00269776A US 3788780D A US3788780D A US 3788780DA US 3788780 A US3788780 A US 3788780A
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US
United States
Prior art keywords
piston
cylinder
ports
open end
dead
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
Application number
US00269776A
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English (en)
Inventor
W Chomczyk
W Chilimoniuk
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wyzsza Szkola Inzynierska
Original Assignee
Wyzsza Szkola Inzynierska
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from PL130193A external-priority patent/PL65706B1/pl
Application filed by Wyzsza Szkola Inzynierska filed Critical Wyzsza Szkola Inzynierska
Application granted granted Critical
Publication of US3788780A publication Critical patent/US3788780A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/04—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports

Definitions

  • the cylinder head carries an outlet with a check valve which closes during the suction stroke so that a partial vacuum is created inside the cylinder until the piston clears the ports to aspirate the fluid; upon the subsequent return stroke, the fluid is discharged through the outlet past the check valve.
  • Our present invention relates to a compressor having a port-and-valve system adapted to eliminate the need for an intake or induction valve.
  • Reciprocating-piston compressors have hitherto been provided with timing system of two distinct types.
  • mechanical or hydraulic means closely couples the movement of the piston with the valve.
  • the opening of the valves is accomplished by the pressure in the cylinder upon reciprocation of the piston.
  • This object can be attained, in accordance with the present invention, which provides a compressor for a working fluid having a cylinder with an open end and a closed end, the closed end being formed with an outlet in which a check valve is provided for preventing induction of fluid.
  • the compressor has no induction or intake valve and comprises a piston extending into the cylinder by the open end as well as drive means for reciprocating the piston toward and away from the closed end so that the piston has a dead-center position remote from the closed end.
  • a valveless annular channel surrounds the cylinder and communicates with the interior thereof by a multiplicity of peripherally spaced inlet ports formed in the cylinder and alternately cut off and uncovered by the piston during each reciprocating stroke thereof, thereby connecting the interior of the cylinder with the channel only as the piston nears its dead-center position mentioned earlier.
  • the inlet ports are spaced above the dead-center position toward the closed end.
  • a valveless supply conduit for the working fluid terminates at the channel and a filter can be provided in the supply conduit.
  • the compressor according to a further feature of the present invention has a stroke which is substantially equal to the piston length so that the inlet orifices remain covered by the piston as it rises and compresses the fluid in the chamber.
  • the bore of the cylinder is about one-fifth larger than its stroke, so that the compression rate is rapid and efficient.
  • the inlet orifices are substantially triangular in shape with their apexes directed longitudinally in the cylinder toward the dead-center position of the piston. In this manner, on retraction of the piston during intake, the piston pulls first beyond the bases of these triangular suddenly exposing a maximum area the intake orifices. Thereafter, since the pressure differential is less, the ratio of intake area uncovered to piston displacement decreases to zero.
  • the intake orifices have an overall surface area which is equal to about one third of the surface area of the piston. These orifices are also spaces above the dead-center or bottom position of the piston by a distance equal to about 15 percent of the piston stroke to ensure that the cylinder is at atmospheric pressure when the piston rises and starts blocking off these intake ports again.
  • FIGURE is an axial cross-sectional view, partly in diagrammatic form, of a compressor embodying the invention.
  • a channel 7 surrounds the cylinder 2 and communicates with the ports 1 via a valveless intake duct provided with a filter 8.
  • a check valve 9 is provided.
  • the piston When the piston is moved downwardly, it creates a vacuum in cylinder 2. As the upper edge of the first ring of the sealing rings 12 and the scraper ring 13 clears the upper edge of ports 1, the cylinder 2 is charged with the medium from the channel 7.
  • the rate at which the fluid enters through the ports 1 is, of course, a function of the pressure differential between the interior of compression chamber 11 and the exterior and is produced by the movement of the piston into its lower deadcenter position past the ports.
  • the time between unblocking of the ports 1 and to the moment at which the piston is shifted upwardly to again close the ports, should be greater than the time required for equalizing the pressure, i.e., charging the cylinder with the medium to be compressed.
  • the upward movement of the piston thus compresses the fluid in chamber 11 and, when the pressure is sufficient, opens valve 9 to discharge the medium into a pressure vessel or pneumatic system.
  • the piston rings 12 also serve to seal the compression space 11 while scaper or lubricating ring 13 scrapes lubricant from the cylinder 2 and prevents penetration of lubricant into the intake ports 1.
  • the triangular ports 1 are isosceles and have a width a which is around two-thirds of their height h and each have and overall area equal to around one-fortieth of the area of the top of the piston 4.
  • the chamber 11 has a bore D which is around 20 percent larger than the length C of the piston 4, which in turn is substantially equal to the stroke E of this piston.
  • the intake manifold 7 is substantially rectangular in cross section with a width 3 slightly smaller, by onesixth, than its height h, giving it a volumetric capacity which is equal to substantially two-fifths that of the cylinder 11.
  • the intake tube from the filter 8 has a height and width i equal to the height h.
  • the lowerscraper ring 13 is spaced above the bottom of the piston 4 by a distance k substantially equal to the distance f so that once the piston 4 has passed the plane P during its compression stroke, these ports 1 will remain blocked until the piston 4 descends to the plane P during the intake stroke. In this manner the pressure in the intake manifold 7 can equalize and the filter 8 is not subjected to the buffeting of any unproductive intake or exhaust steps as is common in prior-art systems.
  • An induction-valve-free compressor for a workingfluid comprising:
  • a cylinder with an open end and a closed end, said closed end being provided with an outlet;
  • a check valve in said outlet adapted to permit said fluid to escape from said cylinder
  • a piston extending into said cylinder and reciprocable between a dead-center position near said open end and a compression position at said closed end;
  • valveless annular channel surrounding said cylinder and communicating with the interior of said cylinder througha plurality of peripherally spaced isosceles-triangular ports formed in the cylinder and spaced above said dead-center position toward said closed end, said ports having bases lying in a common plane orthogonal to the reciprocationaxisof said piston and having apexes directed toward said open end;
  • valveless supply conduit for said working fluid terminating at said channel

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Treatment Of Fiber Materials (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
US00269776A 1968-11-22 1972-07-07 Intake-valve-free compressor Expired - Lifetime US3788780A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PL130193A PL65706B1 (en)) 1968-11-22

Publications (1)

Publication Number Publication Date
US3788780A true US3788780A (en) 1974-01-29

Family

ID=19950254

Family Applications (1)

Application Number Title Priority Date Filing Date
US00269776A Expired - Lifetime US3788780A (en) 1968-11-22 1972-07-07 Intake-valve-free compressor

Country Status (5)

Country Link
US (1) US3788780A (en))
AT (1) AT312783B (en))
DE (1) DE1958927A1 (en))
FR (1) FR2023894A1 (en))
GB (1) GB1296218A (en))

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4560327A (en) * 1982-12-17 1985-12-24 Commonwealth Scientific And Industrial Research Organization Porting and ducting arrangement
US6227815B1 (en) * 1999-06-30 2001-05-08 Campbell Hausfeld/Scott Fetzer Company Pressure control for a reciprocating compressor
US7179060B2 (en) * 2002-12-09 2007-02-20 Caterpillar Inc Variable discharge pump with two pumping plungers and shared shuttle member
US20250257723A1 (en) * 2024-02-12 2025-08-14 Dana Italia S.R.L. Valveless, mechanical, pressure regulating pump

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1002760A (en) * 1909-08-17 1911-09-05 Edward A Rix Air-compressor.
US1342273A (en) * 1919-08-02 1920-06-01 Blache Hans Henrik Lubricating system for internal-combustion engines
US1486651A (en) * 1921-05-05 1924-03-11 Freundlich Erich Refrigerating machine
US2033437A (en) * 1932-02-19 1936-03-10 Bendix Westinghouse Automotive Compressor
US2812893A (en) * 1954-06-28 1957-11-12 Westinghouse Air Brake Co Combined air exhauster and compressor
US2985358A (en) * 1958-02-13 1961-05-23 Winslow Mfg Corp Air pumps
US3065701A (en) * 1956-10-03 1962-11-27 Bessiere Pierre Etienne Self-regulating reciprocating pumps, and in particular in fuel injection pumps for inernal combustion engines

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1002760A (en) * 1909-08-17 1911-09-05 Edward A Rix Air-compressor.
US1342273A (en) * 1919-08-02 1920-06-01 Blache Hans Henrik Lubricating system for internal-combustion engines
US1486651A (en) * 1921-05-05 1924-03-11 Freundlich Erich Refrigerating machine
US2033437A (en) * 1932-02-19 1936-03-10 Bendix Westinghouse Automotive Compressor
US2812893A (en) * 1954-06-28 1957-11-12 Westinghouse Air Brake Co Combined air exhauster and compressor
US3065701A (en) * 1956-10-03 1962-11-27 Bessiere Pierre Etienne Self-regulating reciprocating pumps, and in particular in fuel injection pumps for inernal combustion engines
US2985358A (en) * 1958-02-13 1961-05-23 Winslow Mfg Corp Air pumps

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4560327A (en) * 1982-12-17 1985-12-24 Commonwealth Scientific And Industrial Research Organization Porting and ducting arrangement
US6227815B1 (en) * 1999-06-30 2001-05-08 Campbell Hausfeld/Scott Fetzer Company Pressure control for a reciprocating compressor
US7179060B2 (en) * 2002-12-09 2007-02-20 Caterpillar Inc Variable discharge pump with two pumping plungers and shared shuttle member
US20070086899A1 (en) * 2002-12-09 2007-04-19 Sommars Mark F Fuel system with variable discharge pump
US20250257723A1 (en) * 2024-02-12 2025-08-14 Dana Italia S.R.L. Valveless, mechanical, pressure regulating pump

Also Published As

Publication number Publication date
FR2023894A1 (en)) 1970-08-21
AT312783B (de) 1974-01-25
DE1958927A1 (de) 1970-06-04
GB1296218A (en)) 1972-11-15

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