Title:
OSCILLATORY COMPRESSOR
United States Patent 3597122


Abstract:
An oscillatory compressor having a high pressure chamber with a cylinder thereon and an open-ended tubular piston slidably mounted therein with a pressure responsive valve between the cylinder and the high-pressure chamber providing for passage of compressed fluid from said cylinder to said chamber when the fluid pressure in the cylinder exceeds a predetermined value, and closing the communication therebetween below the predetermined pressure. A pulsating drive for reciprocating the piston including a permanent magnet with poles spaced by an annular airgap and having a movable coil extending into the airgap and drivingly secured to the piston by a free-flow perforated mounting plate providing for unrestricted passage of fluid therethrough from space exterior to the coil and piston into space interiorly thereof. Energization of the coil is provided through one of a pair of opposed springs supporting the piston and coil in a centered position and comprising a contact brush mounted to engage a conductive spring seat mounted on and insulated from the high pressure chamber. The entire assembly is encased in a sealed container with opposed springs resiliently supporting the compressor assembly therein, with a fluid supply inlet into the container from the fluid system, such as a cooling system and a compressed fluid exhaust or withdrawal outlet from the container extending to the high-pressure chamber of the compressor.



Inventors:
FARMER GUY F
Application Number:
04/851806
Publication Date:
08/03/1971
Filing Date:
08/21/1969
Assignee:
GUY F. FARMER
Primary Class:
International Classes:
F04B35/04; F04B39/00; F04B39/10; (IPC1-7): F04B35/00; F04B39/10; F04B35/04; F04B39/00; F04b035/05
Field of Search:
417/363,416,417
View Patent Images:
US Patent References:



Primary Examiner:
Walker, Robert M.
Claims:
I claim

1. A compressor comprising:

2. A compressor as defined in claim 1 wherein said mounting plate is perforated to provide for free passage of fluid therethrough from space exterior to said coil and piston means into space interiorly thereof.

3. A compressor as defined in claim 1 having means for withdrawing compressed fluid from said high-pressure chamber means.

4. A compressor as defined in claim 1 having a sealed container around said compressor, means for supplying gaseous fluid into said container, and means for withdrawing compressed fluid from said high-pressure chamber and out of said container.

5. A compressor as defined in claim 4 having an opposed compressed spring means resiliently supporting said compressor in said container.

6. A compressor comprising:

7. A compressor as defined in claim 6 having means for withdrawing compressed fluid from said high-pressure chamber means.

8. A compressor as defined in claim 6 having a sealed container around said compressor, means for supplying gaseous fluid into said container, and means for withdrawing compressed fluid from said high-pressure chamber and out of said container.

9. A compressor as defined in claim 8 having an opposed compressed spring means resiliently supporting said compressor in said container.

10. A compressor as defined in claim 6 wherein said end plate has a cavity on one side and said headplate has a cavity facing said end plate cavity and forming therewith said high-pressure chamber means.

11. A compressor as defined in claim 10 wherein said end plate has a spring seat in said cavity and said pressure-responsive valve means includes a spring seated on said end plate spring seat and arranged in engagement with said valve means biasing it to closed position on said cylinder end valve seat.

Description:
BACKGROUND OF THE INVENTION

1. Field of the Invention.

This invention relates to fluid compressors or pumps and more particularly to oscillatory compressors of the type driven by a pulsating or reciprocating electromagnetic drive.

2. Description of the Prior Art.

Oscillatory plunger piston type compressors have been used in the past in cooling systems of household refrigerators. In such systems, the oscillatory drive has generally been by an electromagnetic source in which the driving member comprises a coil which reciprocates in an annular airgap between the poles of a permanent magnet and oscillates at the frequency of the exciting current. Opposed compression springs have supported the coil and plunger piston in a central operative position.

SUMMARY OF THE INVENTION

The present invention is an improved oscillatory piston-type compressor wherein the compression of fluid is achieved by an electromagnetically driven open-ended piston axially reciprocated in a cylinder mounted on a high-pressure chamber and having a pressure responsive valve which closes an end of the cylinder open to the high-pressure chamber for pressures in the cylinder below a predetermined value and opens when this pressure exceeds this value. A one-way valve in the end of the tubular piston permits passage of fluid through the piston into space in the cylinder between the end of the piston and the pressure responsive valve during the part of the operating stroke while the piston is being withdrawn from the cylinder and is closed to prevent reverse fluid flow for the opposite stroke while the piston is being moved into the cylinder. Opposed compression springs bias the piston to a predetermined centered position partly out of the cylinder.

The pulsating reciprocating drive of the piston is provided by a coil mounted axially freely oscillatable in an annular airgap between the poles of a permanent magnet and drivingly secured to the piston by an improved mounting plate structure. It has been found that the efficiency and life of this type of pump are both greatly improved by facilitating the free flow of fluid into the piston during the intake or suction stroke. Also, the forces on the mechanism improve its operative life and efficiency if they be substantially balanced in directions transverse to the axial movement of the coil and piston. An important feature of the present improvement is the provision of a fluid free-flow coil mounting plate wherein the plate is perforated by a plurality of openings circumferentially spaced substantially equally around its surface. This eliminates unequal forces transversely of the operating mechanism and minimizes resistance of fluid to the free movement of the coil and piston, and provides for the maximum utilization of the driving force for the compression of the fluid in the cylinder.

Further, the efficiency has been increased by an improved electrical connection of the coil to its source of energization; and the entire mechanism has been greatly silenced in operation by an improved cushioned mounting by resilient compression springs in an outer sealed container into which the fluid is returned before passing into the compressor space around the operating coil and piston.

It is an object of the present invention to provide an improved oscillatory compressor.

Another object of the present invention is to provide an improved and more efficient fluid flow structure in an oscillatory compressor.

A further object of the present invention is to minimize the noise and vibration produced by an oscillatory compressor.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a schematic representation of a refrigerating system provided with an embodiment of the present invention;

FIG. 2, a longitudinal sectional view through the compressor shown in the FIG. 1 system including embodiments of the improvements of the present invention;

FIG. 3, a sectional view taken along line 3-3 of FIG. 2 illustrating the improved mounting plate;

FIG. 4, an enlarged sectional view of the compression section of the cylinder and adjacent end of the piston with the cooperating one-way valve and pressure responsive valve during an intake or suction stroke;

FIG. 5, a sectional view of the FIG. 4 structure illustrating the parts during a compression stroke; and

FIG. 6, an enlarged sectional view, partly broken away, taken along line 6--6 of FIG. 4, showing details of the one-way valve.

DETAILED DESCRIPTION OF THE INVENTION

Referring to the drawings, an embodiment of an improved oscillatory compressor 10 according to this invention is shown in FIG. 1, connected by a high-pressure fluid pipe or tube 11 to a suitable refrigerating system condenser 12. The condenser 12 is connected by a suitable tube or pipe 13 to an evaporator 14 where the fluid expands and is vaporized, producing its ambient cooling effects. The vaporized gaseous fluid then passes through a tube or pipe 15 back into a sealed container 16 of the compressor 10, where the fluid is recompressed and recycled through the pipe 11 and the rest of the system.

Details of the compressor are more clearly shown in FIGS. 2--6. In the illustrated embodiment, the sealed container 16 and the compressor therein are adapted to operate with the longitudinal axis thereof vertical. This is important as the oscillation of the mechanism is along this longitudinal axis and special resilient cushioning of the compressor in the casing along this axis provides an exceptionally quiet, vibrationless device. The casing 16 may be made of any suitable material, such as pressed steel, and includes a main body portion with an open end and a closed end 16'. The open end is adapted to be sealed and closed after the compressor is assembled therein and the closure may comprise any suitable member, such as a cover 17 fitted over a gasket 18 and secured in position in any suitable manner, as by screws 19. The compressor is cushioned and resiliently mounted in the container 16 by a pair of opposed compression springs 20 and 21, respectively seated on spring seats 22 and 23 pressed in the ends 16' and 17 of the container and engaging opposite ends of the compressor. This provides a very efficient cushioned support for the compressor and permits it to operate as a fully self-contained unit without affecting or being affected by other parts of the system or nearby units.

The compressor includes an end plate 24 formed with a spring seat 25 on one side against which the compression cushioning spring 20 is seated. This end plate is formed with a cavity 26 on the side opposite the spring seat 25 and is sealingly secured by a plurality of bolts 27, in engagement with a gasket 28, to a headplate 29. The head plate 29 preferably is formed with a cavity 30 facing and communicating with the end plate cavity 26 and forming therewith a high-pressure chamber for receiving fluid compressed by the compressing mechanism.

This compressing mechanism includes a cylinder 31, shown formed integral with the headplate 29, with the lower end thereof formed with a valve seat 32 and open into the high-pressure chamber. A pressure-responsive valve, comprising a retained and spring seat member 33 with a valve 34 thereon, is resiliently biased by a predetermined spring pressure against the cylinder valve seat 32 by a compression spring 35 seated on the valve spring seat 33 and a spring seat 36 formed in the cavity 26 on the end plate 24. In this manner, the cylinder 31 is closed to the high pressure chamber for all pressures below a predetermined valve and is opened to the high-pressure chamber by the valve 34 when the compressed fluid in the cylinder is above this predetermined valve. FIGS. 4 and 5 respectively show the closed and open valve conditions.

Compression of fluid in the cylinder 31 is done by a plunger-type open-ended tubular piston 37 which is axially slidably fitted in the cylinder 31 through the end thereof opposite the pressure chamber end. The lower end of the piston 37 is provided with a one-way valve mechanism comprising an axially displaceable valve 38 loosely movably mounted in a valve housing 39 secured to the end of the piston 37 by threaded engagement therewith. The valve housing is formed with a valve retaining ring 39', FIGS. 4, 5 and 6, which has a central opening diameter greater than the diameter of the main central body of the valve 38, FIG. 6. The valve is formed with a plurality of outwardly extending fingers 38' which project over the retaining ring 39' and allow free passage of fluid from the piston 37 into the cylinder 31 between the fingers 38' through the space between the outer periphery of the body of the valve 38 and the inner periphery of the retaining ring 39' when the valve is in its lower position as shown in FIG. 4. The diameter of the main body of valve 38 is greater than the diameter of the bore of tubular piston 37 so that when the valve is moved to its upper position, as shown in FIG. 5, when the fluid pressure in the cylinder 31 between the valves 34 and 38 is higher than the fluid pressure in the bore of the piston 37, the valve 38 effectively closes the end of the piston bore and prevents reverse flow of fluid from the cylinder 31 into the piston 37. These two positions of valve 38 result as the piston is moved respectively away from and toward the high pressure chamber end of the cylinder 31.

This reciprocating movement of the piston is provided by an oscillatory or pulsating drive comprising a suitable permanent magnet having a pair of pole face pieces 41 and 42 concentrically secured together, as by a pin 43 fastened by any suitable means, such as retainer rings 44 and 45 in engagement with grooves in the pin 43. The pole pieces form concentric poles spaced by an annular airgap 40', the uppermost pole piece 41 being in the form of a depending sleeve which surrounds and extends slightly beneath the lower pole piece 42, and a coil is placed axially movable in this airgap. This coil is preferably wound on a plurality of axially extending fingers 47 secured to a mounting plate 48 which is rigidly secured to the end of the piston 37 opposite the one-way valve 38, thus providing a driving connection between the coil 46 and the piston 37.

Opposed spring means, comprising a pair of electrically conductive compression springs 49 and 50, support the coil 46 and piston 37 centered respectively partially axially out of the airgap and cylinder. The upper spring 49 is seated on a spring seat formed on the lower side of the magnet pole face piece 42 and on a spring seat formed on a shoulder 48' on the mounting plate 48. The lower spring 50 forms part of the electrical circuit for energizing the coil 46. This circuit includes a connecting ring 51 mounted on an insulating bushing 52 on the mounting plate 48 which forms the upper spring seat for the spring 50. This ring 51 is provided with an outwardly projecting tab 53 to which the coil is electrically connected through lead 54. The bottom of spring 50 is seated on a spring seat formed by a connecting ring 55 mounted on an insulating bushing 56 on the headplate 29, thereby forming an electrical circuit between the two rings 53 and 55. Electrical energization is provided to the coil 46 through the rings and spring by a sliding brush-type contactor 57 connected to a terminal 58 mounted on an enclosing casing 59 by an insulating bushing 60 to which a supply lead 61 is connected. This supply lead extends out through the container 16 and is adapted to be connected to a suitable alternating current supply. The casing 59 is fitted into grooves in the inner ends of pole facepiece 41 headplate 29 and the entire assembly is rigidly secured together by a plurality of through bolts 62 which extend through the headplate 29 and threadedly engage the end of the pole facepiece 41 with the bolt heads in sockets in the headplate.

As previously explained, the gaseous fluid is returned to the container 16 through the tube 15. It then passes from the container 16 through a tube 63 into the space within the casing 59. Energization of the coil 41 by alternating current alternately biases the coil into and out of the airgap 40' against the centering action of the opposed springs 49 and 50 at the frequency of the alternating current, whereby the piston 37 is respectively reciprocated away from and toward the end of the cylinder open to the high-pressure chamber 30. As the piston moves outwardly from the cylinder, a suction is created in the bore of the piston and the one-way valve 38 moves to its lower position, FIG. 4, so that fluid in the piston bore flows into the cylinder through the opening between the valve fingers 38'. This fluid must be drawn into the interior of the piston from fluid within the space inside the coil 46. A small amount of fluid can pass from the exterior of the coil to its interior over the upper edge of the coil in the airgap 40, but this is a rather restricted passage. An important feature of this invention is the improved inlet structure provided by a plurality of perforation 48" formed around the mounting plate 48. These provide for an even free flow of fluid into the coil interior and from thence into the piston bore with substantially no resistance to the operation. Alternate movement of the piston into the cylinder 31 causes the valve 38 to move to its upper position and prevents reverse flow of fluid out of the piston. This movement compresses fluid in the cylinder 31 to a pressure above the predetermined pressure and causes the pressure responsive valve 34 to open, FIG. 5, so that the compressed fluid passes out of the cylinder into the high pressure chamber 30. The exhaust tube 11 extends into the container 16 and passes through the end plate 24 into the high-pressure chamber cavity 26 so that the compressed fluid can pass out through the tube 11 as it is needed in the system.