US3276673A

US3276673A - Contaminant free compressor

Info

Publication number: US3276673A
Application number: US279585A
Authority: US
Inventors: Jones John Roger; Maciej J Makowski
Original assignee: Fairchild Hiller Corp
Current assignee: Fairchild Hiller Corp
Priority date: 1963-05-10
Filing date: 1963-05-10
Publication date: 1966-10-04
Anticipated expiration: 1983-10-04

Description

Filed May 10, 19 3 J. R. JONES ETAL CONTAMINANT FREE COMPRESSOR Oct. 4, 1966 INVENTOR5 JOHN ROGER J'ONES MAC/EJ J'EAZY MAKOWS/(l BY ATTOE VL Y'S United States Patent 3,276,673 CONTAMINANT FREE COMPRESSOR John Roger Jones, Manhattan Beach, and Maciej J. Ma-

kowski, Torrance, Calif., assignors to Fairchild Hiller Corporation, a corporation of Maryland Filed May 10, 1963, Ser. No. 279,585 9 Claims. (Cl. 230-20) This invention relates to compressors and more particu-larly to contaminant free compressors and control systems therefor.

It is an object of this invention to provide a compressor in which the compressed medium or media are kept free of contaminants.

A further object of the invention is to provide a dual stage compressor for two different gases.

Still another object of the invention is to provide a compressor having a plurality of stages in which the compressor actuating fluid and the compressed media are segregated to keep the compressed media contaminant free.

A further object of the invention is to provide a dual stage compressor for two gases in which the gases are segregated from the compressor actuating fluid by resilient diaphragm members, the actuating fluid flow being regulated by a servo system.

Other objects and advantages of the present invention will become more apparent upon reference to the following specification and annexed figure.

In the present invention a compressor system having high efficiency performance capability is obtained through the use of what is termed a multiple stage duplex system. The compressor is adapted to compress two separate and distinct gases in .a plurality of stages and the compressed gases may then be utilized in cooperation with other elements, such as in a refrigeration cycle. The compressor of the present invention uses a plurality of hydraulically actuated compressor elements which have a barrier in the form of a resilient diaphragm to segregate the compressor actuating fluid from the compressed medium. This assures that the compresser medium will not become contaminated with foreign substances or particles. Addi tionally, the present invention includes a hydraulic servo system to correlate and automatically regulate the interaction of the actuating fluid driving mechanism and the diaphragmed compressor elements. A compressor of the type disclosed herein, due to its high efficiency and other advantageous factors is ideally suited for use in high performance cooling systems that are generally categorized as extremely low temperature or cryogenic systems.

The compressor, actuating mechanism and control system is schematically illustrated in the figure. A two stage system is shown for operating with two separate and distinct gas supplies 4 and 5. These supplies may contain the same or different gases which may be, for example, nitrogen and hydrogen respectively. The primary or first stage compressor elements are designated by the reference numerals and 10a and are each connected to respective gas supply source 4 and 5. The secondary stage compressor elements, designated by the reference numerals as 10b and 100, are arranged to cooperate with the respective

primary compressor elements

10 and 100. This dual stage operation contributes an important factor to the exceptionally high performance characteristics of the present device.

*Each of the four compressor elements 10', 10a, 10b, and 100 is of the diaphragm type and of substantially the same configuration, the only variation being in the sizing of the primary stage and secondary stage elements. The description which follows applies to all four compressor elements 10, 10a, 10b, and 10c.

3,276,673 Patented Oct. 4, 1966 "ice Each of the compressor elements is provided with a respective resilient diaphragm member 14, 14a, 14b and 14c which is situated within a cavity having walls 21 and 21a formed in a

respective housing

16, 16a, 16b and 16c. The resilient diaphragms are prefer-ably of metal although other suitable material may be used. For purposes of clarity, each diaphragm member is shown in a middle position within its respective cavity to clearly illustrate the fact that a diaphragm segregates its cavity into two distinct chambers. The respective chambers 18, 18w, 18b and 180 on one side of the diaphgrams are exposed to the media to be compressed while the chambers 20, 20a, 20b and 200 on the other side of the diaphragms are exposed to an actuating fluid. The shape of each cavity is such that it will readily accommodate the shape of its diaphragm when the diaphragm is deflected in one direc tion or the other.

The chambers 18, 18a, 18b and 180 formed between one side of a respective compressor element and resilient member 14, 14a, 14b and 14c form portions of two closed loop gas systems. In the present arrangement which is illustrative of a cascaded closed cycle high performance refrigeration system, the chambers 18 and 18c of the compressor elements 10, form part of a first gas circuit while the chambers 18a and 18b of the compressor elements 10a and 10b are part of a separate second gas circuit.

Each of the

elements

10, 10a, 10b and 100 is provided with a respective gas inflow valve 11, 11a, 11b and and a

gas outflow valve

12, 12a, 12b and 120. The valves are schematically illustrated as being conventional spring loaded check valves. Inlet valves 11 and 11w are between the respective sources 4 and 5 and compressor elements 10- and 10a while valves 11b and 11c control the flow of gas from the elements 10 and 10a to the respective elements 100 and 10b. The outflow valves 12, 12a, 12b and are utilized to facilitate the exit of gases being compressed from a respective gas chamber 18, 1=8a-, 18b and 180. Valves 12b and 120 communicate with the utilization devices 7 and 8 which may be, for example,

cryostats.

A plurality of conduits are arranged to permit the inflow and outflow valves just mentioned to communicate. There, the gases compressed in the primary stage compressors 10 and 10a are directed through outflow valves 12 and 12a by means of conduits 6 and 6a to the corresponding inflow valves 11b and 110 of the second stage compressors.

The surfaces of the resilient diaphragm members 14, 14a, 14b and in the respective chambers 20, 20a, 20b and 200 are exposed to an actuating fluid. When the fluid is directed against a diaphragm member under suflicient pressure to overcome the resiliency of the diaphragm and the pressure of the gas in the respective chamber on the other side of the diaphragm, the diaphragm is dis placed until it abuts the extremity 21a of the cavity on the chamber side holding the gas. This compresses the gas and directs it through the outflow valve of the compressor element. In this manner eachcompressor element in the system performs its function of increasing the pressure of the [gas in its particular circuit or loop.

The compressor elements are operated in a two stage sequence by an actuating fluid pumping mechanism 40'. The pumping mechanism is driven by some external means which may, for example, take the form of an electric motor (not shown). The pumping mechanism is located in a housing 42 and includes a pair of

stepped pistons

44, 44a, and 46, 46a which are fixed to and disposed on either side of a yoke member 48. If desired individual piston and yoke drives may be used instead of the dual arrangement shown. Connected to the yoke member 48 to impart a reciprocal motion thereto, is

an eccent'rically mounted drive shaft 50. The shaft is driven by an external power source.

When the shaft 50 is rotated, the yoke member 48 and the other associated mechanisms including

stepped pistons

44, 44a and 46, 46a are caused to reciprocate within correspondingly stepped and stationary upper and

lower cylinder heads

38, 38a and 36, 36a respectively. In this manner the reciprocating pistons within the stationary cylinders cooperate to alternately pump, in well known fashion, an actuating fluid, such as oil, from a reservoir 60, first to one stepped cylinder head which accommodates pistons 44 and 44a and then the oppositely disposed cylinder head which accommodates stepped piston 46, 46a. The fluid in reservoir 60 is kept under pressure by a bellows 35.

The pumping system provides for the pumping of fluid by the undersurfaces of the

wider area pistons

44 and 46, within a control portion of the housing 42, which will hereinafter be referred to as the crankcase 42a. .Pistons 44 and 46 pump the actuating fluid through an outlet port 41 in the crankcase 42 and then thence through a conduit into a cooling element 39. The actuating fluid dissipates heat in the cooling element 39 before being delivered through a check valve 37 into the fluid reservoir 60.

As illustrated in the drawing, conduit 33 and its associated check valve 31 parallels the cooling element 39 and provides for the dire-ct communication of actuating fluid between the fluid reservoir 60 and the crankcase 42a of the pumping mechanism. In this connection, it should :be noted that the actuating fluidcools, by contact with the resilient diaphragm members in the compressor elements, the gases being compressed. This cooling' arrangement, which is inherent in the compressor system, removes most of the heat of compression from the gas. However, a portion of the actuating fluid is continuously circulated through the cooler 39 thereby maintaining the fluid temperature and all other related mechanisms at a relatively constant desirable temperature, which is unusually low for compressors of comparable performance.

The fluid chambers 20 and 20b of compressor elements 10 and 10b, which correspond respectively to the first stage compressor for a first gas compression loop (source 4) and the second stage compressor for a second gas compression loop (source 5) respectively, are adapted to communicate with the upper stepped cylinder heads '38 and 38a respectively. The plston member 44, 44a is accommodated within the stepped cylinder 38, 3811 so that when the piston moves into these cylinders, pressure is transmitted to the actuating fluid. This displaces the fluid and causes it to exert force on the resilient diaphragm members 14, 14b of the compressor elements and 10b. Consequently, the diaphragms 14 and 14b are caused to deflect thereby affecting compression of the gases in their respective chambers 18 and 181).

Since the opposite extremity of the pumping mechanism is equipped with the stepped piston 46, 46a which is accommodated with the stepped cylinder 36, 36a, when the piston is actuated through the yoke mechanism in the direction opposite to that just described, actuating fluid is compressed thereby and delivered in similar fashion to the diaphragms 14a and 140 of the compressor elements 10a: and 10c. This causes the gases in the respective chamber 18a and 180 to be compressed thereby operating the second stage of the first loop and the first stage of the second loop.

The injection of hydraulic fluid into the cylinder heads of the actuating pump mechanism 40 is of great importance to the overall efliciency of the compressor mechanism. Accordingly, a fluid metering system is provided to effectively control the admission of actuating fluid to the cylinder heads so that the piston elements are not required to pump more fluid than is necessary to actuate the compressor elements and supply actuating fluid to a selfregulating servo control system.

To carry out the fluid metering uni-directional check valves 19 and 19a are provided for the two primary stage compressor elements 10 and 10a. These check valves are shown as being of the conventional spring loaded variety which operate in well known fashion to overcome the spring force and permit flow when suflicient force has been applied against the valve sealing member 29. Additional check valves 27b and 27c are provided to cooperate with the second stage compressor elements 10b and 10c to regulate the inflow of actuating fluid to the .reduced area portions of the stepped cylinders of the actuating fluid pump which are connected to the actuating fluid chambers 20b and 20c of the second stage compressor elements. Each of the check valves 19, 19a and 27b, 270 is arranged to communicate with a respective actuating fluid chambers 20, 20a, 20b and 200 and operate to direct actuating fluid to respectively connected fluid metering valves 50, a, 50b, and 500 disposed between the actuating fluid chambers of the compressor elements and the actuating fluid supply reservoir 60.

Since the primary function of the relief check valves 19, 19a, 27b and 27c is to bypass that fluid under pressure not actually required to drive the diaphragm of the respectively connected compressor elements, each valve is effectually responsive to the pressure of the gas being compressed in the respectively connected element. For this reason the relief valves 27b, 27c associated with the second stage of compression elements 10b and 100 are of modified configuration and consequently are better able to accommodate the extremely high pressures in the second stage compression without the attendant need to subject the compressor element diaphragm members to excessive stresses. To accomplish this the valves 27b, 270 which perform a function comparable to that of the previously described Valves 19 and 19a are provided with resilient diaphragms 25 which are exposed on one side to the pressure of the gases being compressed in the second stages of compression and additionally biased in the same direction by a spring force provided by springs 28. These forces are opposed by the actuating fluid pressures which are communicated from the fluid chambers of the second stage compressor elements to the opposite sides of diaphragms 25 of each valve 27b, 27c. Consequently the force unbalance on either side of the diaphragms 25 causes the diaphragms 25 to assume a reference position with respect to a respective fluid outflow port 30 thereby aifecting a throttling action and regulating the flow of actuating fluid which is permitted to escape through the port 30 and through suitable conduits to the fluid metering valves 50b and 500.

The metering of actuating fluid to the various cylinders of the actuating pump 46 is related to the position of the control elements of the metering valves. These valves affect the amount of flow of actuating fluid from the reservoir supply 60 to the respective cylinders. Each of the

metering valves

50, 50a, 50b and 500 is identical in function as well as configuration and for this reason a description of one suflices for all.

' The metering valve 50 is provided with fluid inflow ports 53 and 55 which are in communication with the pressurized fluid reservoir 60. An outflow port 56 communicates between valve 50 and the upper fluid pump cylinder head. Interposed between the inflow and outflow ports is a variable position double spool 52, 54 which is adapted to be biased in one direction by a spring 51 and in the opposite direction by the fluid pressure communicatedfrom the connected bypass valve 19. It will be noted that the undersurface of the spool 52 is provided with a chamfer which in combination with the outflow port provides a modulated fluid flow to the cylinder 38. It will be further noted that the inflow ports 53 and 55 are so disposed with relation to the spool, that when the spool is in one extreme position the spring 51 is fully extended valves 19a, 27b and 270.

. pressure.

and the'flow from the inflow ports to the outflow port is unimpeded. Such is the condition upon start up, prior to the time when the fluid pump generates fluid pressure.

Once in operation however the fluid bypassed by the valve 19 reacts against the undersurface of spool 52 tending to counteract the spring force and modulate the posi- .tion of the spool accordingto the amount of flow of actuating fluid communicated from the fluid chamber 20 of the compressor element 10.

The spools 52 of the other metering valves 50a, 50b and 500 are controlled by the fluids in the respective chambers 20a, 20b and 20c of the elements a, 10b and 100 only the necessary amount of fluid is. pumped. This con- .tributes to the high efliciency of the system.

A typical cycle of operation of the system will now be described. With the machine at rest the closed loop gas circuit, which in the present system contains gas under pressure, causes the gas chambers 18, 18a of the first stage compressor elements 10 and 10a, and chambers 18b, 18c of the second stage compressor elements 10b and 10c to become filled by virtue of the respective inflow valves 11, 11a, 11b and 110. Additionally, the relief valves 27b, 27c will be pressurized by the gas. Therefore, the resilient diaphragm members in each compressor element as well asthe diaphragm members 25 in the relief valves 27 b, 270, these members not being influenced by actuating fluid due to the inaction of the pump, are deflected by the gases and bedded against the surfaces 21 of each of their respective cavities.

Since fluid actuating pressure will not be generated by the pump until the drive shaft'is rotated, the spools of each of the metering valves 50, 50a 50b and 50c will be dead ended against their respective housings with the springs 51 fully extended. In this manner the actuating fluid under slight pressure from the reservoir 60 by virtue of bellows 35 is permitted to flow unimpeded through the metering valves 50 and 50b thereby filling the vacant cylinder heads 38a and 38.

As the drive shaft 50 is rotated and the stepped piston 44, 44a moves into-the cylinder heads 38-, 38a, actuating fluid is displaced and directed against the diaphragm 14,

14b of the first stage-first gas loop and second stage-second gas loop compressor elements 10, 10b. When the pressure of the actuating fluid is suflicient to overcome the resistance offered by the gas pressure against the resilient diaphragms 14 and 14b, the diaphragms are displaced until they come to rest against the opposing surfaces 21a of their respective cavities. Consequently the gas in chamber 18 of the first compression stage and the gas in chamber 18b of the second compression stage overcome the set point of their respective outflow valves 12, 12b permitting the gasesnow compressed to a higher.value, to exit into their respective loops.

It must be remembered that the actuating fluid pump capacity is greater than that required to displace the compressor diaphragms 14, 14b so that when said diaphragms have reached their limit of travel the actuating fluid pressure in the fluid chambers 20 and 20b rapidly increases until the spring pressure of relief valve 19 and the spring pressure in the bypass valve 27b are overcome, permitting fluid flow through these valves. The flow of actuating fluid in valves 19 and 27b is then directed into the metering valves 50 and 501) against the upper surface of the spools 52 in the manner previously described. Consequently the position of the spools within the valve body and particularly with respect to the fluid inflow ports 53 and 55 and the outflow port 56 is modified thereby influencing and reducing the further flow of fluid into the cylinders of the pump.

.cavity being separated from each other by' said It should be appreciated that the foregoing description of operation related only to. a single upward stroke of the piston elements. However, a single stroke in the opposite direction would produce the same result with the alternately disposed gas compression elements .and actuating fluid circuitry. Of course it is understood that continued operation of the mechanism produces rapid strokes. first in one directionthen the other thereby enabling the two gases to be compressed, one of the gases through the first stage and the other gas through the second stage of compression while during the opposite stroke of the pump the first and second compression stages of the two gases are alternated.

Of course it will be appreciated that the arrangements provided herewith contain many underlying advantages and improvements which cooperate to provide a contaminant free compressor that is capable of operational performance that had not heretofore been possible.

Additionallyit should be understood and appreciated that the mechanism heretofore described and shown is by way of example only and obviously many changes and alternatives may be utilized without departing from the spirit of the invention.

What is claimed is:

1. A duplex compressor system for operation with first and second working fluid sources comprising first and second independent closed fluid loops, a pair of first compressor elements, a pair of second compressor elements, each of said compressor elements being formed by a housing having a cavity which is divided into two chambers by a resilient diaphragm member, said first compressor elements providing low compression relative to said second compressor elements, one chamber of one of said first and second compressors forming a portion 'of one of said closed loops and one chamber of the other of said first and second compressors forming a portion of the other of said-closed loops, means for --supplying actuating fluid to the other chamber of each said element, and means for pumping said actuating fluid toalternately depress simultaneously the diaphragm -members of said first element in said first loop and said second element in said second loop and then depress simultaneously the diaphragm members of said second element in said first loop and said first element in said second loop, thereby compressing the working fluid therein, the actuating. fluid and the working fluid in each resilient diaphragm.

2. A duplex gas compressor system as set forth in claim 1 wherein said resilient diaphragm member is made of a heat conductive material so that heat is transferred .from the gas to the actuating fluid in each cavity.

-means for supplying actuating fluid and said pumping -means and respective to the working fluid pressure in at least one compressor element for controlling the amount of actuating fluid supplied to said pumping means.

4. A duplex compressor system as set forth in claim 3 further comprising means in each of said first and second closed fluid loops for sensing the pressure of the working fluid in the respective loop, and means connecting said sensing means to said means for controlling the amount of actuating fluid supplied.

5. A duplex gas compressor system comprising first and second closed gas loops, each of said first and second loops having respective first and second compressor elements, each of said compressor elements being formed by a housing having a cavity which is divided into two chambers by a resilient diaphragm member, means for supplying gas to one chamber of each compressor element, a source of actuating fluid for the other chamber of each said compressor element, the actuating fluid and the gas in each cavity being separated from each other by said resilient diaphragm, means for pumping said actuating fluid under pressure to each compressor element to depress the diaphragm member in each compressor cavity thereby compressing the gas therein, a relief valve means connected to the gas chamber of each said compressor and responsive to the gas pressure therein, a refluid and said pumping means and actuated by the re spectively connected relief valve means to control the amount of actuating fluid supplied from the source to the pumping means.

6. A duplex gas compressor system comprising first and second closed gas loops, each of said first and second loops having respective first and second compressor elements, each of said compressor elements being formed by a housing having a cavity which is divided into two chambers by a resilient diaphragm member, means for supplying gas under pressure to one chamber of each compressor element, a source of actuating fluid for the other chamber of each said compressor cavity, the actuating fluid and the gas in each cavity being separated from each other by a resilient diaphragm, and pumping means operating to alternately pump actuating fluid under pressure from the fluid source to the first compressor element of the first loop and the second element of the second loop and then to the second element of the first loop and the first element of the second loop to compress the gas in each respective chamber.

7. A duplex gas compressor system comprising first and second closed .gas loops, each of said first and second loops having respective first and second compressor elements,

each of said compressor elements being formed by a the fluid source to the first compressor element of the first loop and the second element of the second loop and then to the second element of the first loop and the first element of the second loop to compress the gas in each respective chamber, and means connected between said source of actuating fluid and said pumping means and responsive to the gas pressure in at least one compressor element for controlling the amount of actuating fluid supplied to said pumping means.

8. A duplex gas compressor system comprising first and second closed gas loops, each of said first and second loops having respective first and second compressor elements, each of said compressor elements being formed by a housing having a cavity which is divided into two chambers by a resilient diaphragm member, means for supplying gas under pressure to one chamber of each compressor element, a source of actuating fluid for the other chamber of each said compressor cavity, the actuating fluid and the gas in each cavity being separated from each other by a resilient diaphragm, pumping means operating to alternately pump actuating fluid under pressure from the fluid source to the first compressor element of the first loop and the second element of the second loop and then to the second element of the first loop and the first element of the second loop to compress the gas in each respective chamber, means in each of the first and second gas loops for sensing the pressure of the gas in the respective loop, and means connected between said source of actuating fluid and said pumping means and actuated by said pressure sensing means to control the amount of actuating fluid supplied to said pumping means.

9. A duplex gas compressor system comprising first and second closed gas loops, each of said first and second loops having respective first and second compressor elements, each of said compressor elements being formed by a housing having a cavity which is divided into two chambers by a resilient diaphragm member, means for supplying gas under pressure to one chamber of each compressor element, a source of actuating fluid for the other chamber of each said compressor cavity, the actuating fluid and the gas in each cavity being separated from ecah other by a resilient diaphragm, pumping means operating to alternately pump actuating fluid under pressure from the fluid source to the first compressor element of the first loop and the second element of the second loop and then to the second element of the first loop and the first element of the second loop to compress the gas in each respective chamber, a relief valve means connected to the gas chamber of each said compressor element and responsive to the gas pressure therein, a respective metering valve means connected to and operated by each said relief valve means, the said metering valve means being connected between said source of actuating fluid and said pumping means and actuated by the respectively connected relief valve means to control the amount of actuating fluid supplied from the source to the pumping means.

References Cited by the Examiner UNITED STATES PATENTS 2,092,717 9/1937 Iodry 230-53 2,593,255 4/ 14952 Bowman 103-44 2,752,854 7/1956 Prior et al. 10344 2,919,650 1/1960 Wiggerman 103-44 2,970,747 2/1961 Kaspar et al. 230-45 2,982,466 5/1961 Pier 230-20 FOREIGN PATENTS 449,979 7/ 1948 Canada.

864,365 1/ 1941 France. 1,188,148 3/1959 France. 1,188,239 3/1959 France.

MARK NEWMAN, Primary Examiner.

DONLEY J. STOCKING, Examiner.

W. L. FREEH, Assistant Examiner.

Claims

1. A DUPLEX COMPRESSOR SYSTEM FOR OPERATION WITH FIRST AND SECOND WORKING FLUID SOURCES COMPRISING FIRST AND SECOND INDEPENDENT CLOSED FLUID LOOPS, A PAIR OF FIRST COMPRESSOR ELEMENTS, A PAIR OF SECOND COMPRESSOR ELEMENTS, EACH OF SAID COMPRESSOR ELEMENTS BEING FORMED BY A HOUSING HAVING A CAVITY WHICH IS DIVIDED INTO TWO CHAMBERS BY A RESILIENT DIAPHRAGM MEMBER, SAID FIRST COMPRESSOR ELEMENTS PROVIDING LOW COMPRESSION RELATIVE TO SAID SECOND COMPRESSOR ELEMENTS, ONE CHAMBER OF ONE OF SAID FIRST AND SECOND COMPRESSORS FORMING A PORTION OF ONE OF SAID CLOSED LOOPS AND ONE CHAMBER OF THE OTHER OF SAID FIRST AND SECOND COMPRESSORS FORMING A PORTION OF THE OTHER OF SAID CLOSED LOOPS, MEANS FOR SUPPLYING ACTUATING FLUID TO THE OTHER CHAMBER OF EACH SAID ELEMENT, AND MEANS FOR PUMPING SAID ACTUATING FLUID TO ALTERNATELY DEPRESS SIMULTANEOUSLY THE DIAPHRAGM MEMBERS OF SAID FIRST ELEMENT IN SAID FIRST LOOP AND SAID SECOND ELEMENT IN SAID SECOND LOOP AND THEN DEPRESS SIMULTANEOUSLY THE DIAPHRAGM MEMBERS OF SAID SECOND ELEMENT IN SAID FIRST LOOP AND SAID FIRST ELEMENT IN SAID SECOND LOOP, THEREBY COMPRESSING THE WORKING FLUID THEREIN, THE ACTUATING FLUID AND THE WORKING FLUID IN EACH CAVITY BEING SEPARATED FROM EACH OTHER BY SAID RESILIENT DIAPHRAGM.