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Publication numberUS3838942 A
Publication typeGrant
Publication dateOct 1, 1974
Filing dateJul 19, 1973
Priority dateJul 30, 1971
Publication numberUS 3838942 A, US 3838942A, US-A-3838942, US3838942 A, US3838942A
InventorsF Pokorny
Original AssigneeMitchell J Co
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Refrigeration compressor
US 3838942 A
Abstract
A blow-by lubricating system for refrigerant compressors is provided in which refrigerant entrained oil is circulated by blow-by action from the oil sump, over and through all of the rotating input bearings and parts such as the rotor, wobble plate and input shaft assembly back through a wall of the compressor housing into the refrigerant input chambers of the compressor, and thence into the refrigerant stream and in part back to the oil sump through the compressor cylinders. The circulation is constrained over the rotating input bearings and parts in such a manner that a substantial portion of the entrained oil is centrifugally separated from the refrigerant and maintained in the oil sump. This minimizes the amount of oil entrained in the refrigerant, thereby increasing compressor efficiency while enhancing its lubrication. A properly sized "dumping orifice" is provided connecting the oil sump directly to the input chambers of the compressor. The function of this orifice is to remove excess oil trapped in the oil sump due to centrifugal separation at high rotative speeds and thereby to preclude overheating of the compressor.
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Oct. 1, 1974 i 1 REFRIGERATION COMPRESSOR [75] Inventor: Frederick E. Pokorny, Sherman, i g ggf rx i qibg gf ex Attorney, Agent, or Firm-Herbert M. Blrch; Terrell [73] Assignee: John E. Mitchell Company, Dallas, C, Bir h; Anthony L, Birch Tex.

[22] Filed: July 19, 1973 [57] ABSTRACT [21] App]. No.: 380,533

Related U S Application Data A blow-by lubricating system for refrigerant compres- 63 sors is provided in which refrigerant entrained oil is csntgluattljon of Ser. No. 167,639, July 3 1971 circulated by blow-by action from the oil sump, over a an one and through all of the rotating input bearings and parts such as the rotor, wobble plate and input shaft 5 assembly back through a wall of the compressor hous- [58] Fie'ld /84 192 ,5 468 ing into the refrigerant input chambers of the com- 184/6 16 6 4177269 270 437 439 p r, and thence into the refrigerant stream and in 441 i U 2 part back to the oil sump through the compressor cylinders. The circulation is constrained over the rotating [56 1 References Cited input bearings and parts in such a manner that a substantial portion of the entrained oil is centrifugally UNITED STATES PATENTS separated from the refrigerant and maintained in the 1,731,774 10/1929 Gurley 417/439 oil sump, This minimizes the amount of oil entrained 1,916,130 6/1933 Torrey 417/441 i h f ig r nt, thereby increasing compressor ffi- 2,256,926 9/1941 Manlscalco 417/439 ciency while enhancing its lubrication A properly l f sized dumping orifice is provided connecting the oil 30855l4 M1963 i e a 417 M03 sump directly to the input chambers of the compres- 3l23287 3/1964 417/439 sor. The function of this orifice is to remove excess oil 3:151:527 10/1964 Hamlin 417/269 trapped in the Oil p due Centrifugal Separation 3,215,341 11/1965 Francis 417/269 at hig otative speeds and thereby to preclude over- 3,411,453 11/1968 Chanal 417/269 heating of the compressor. 3,557,664 l/l971 Akaike 417/269 3,587,406 Gannaway 417/437 Claims 4 Drawing Figures FOREIGN PATENTS OR APPLICATIONS 304,555 l/l929 Great Britain 74/60 Q 56A |2 58 12 30 I8 14 h\\\\\\\ 56 46 5o ,I6A

I 3s 7 745 a,

5Q 2Q l6A A lffif i E: ll BL 15 PATENIEDHU 1 I574 ENE 187 2 INVENTOR FREDERICK E. POKORM j 6% HEM ATTORNEY PMEME BBI H974 KEW INVENTOR FREDERICK E. 'POKORNY BY @M Q 1 M ATTORNEY REFRIGERATION COMPRESSOR This is a continuation of application Scr. No. 167,639. filed July 30. I971.

SPECIFICATION This invention relates to refrigerant compressors, and more particularly, to refrigerant compressors of the automotive type having a new and novel positive lubrication system.

In automotive air conditioning systems. lubricating oil and refrigerant circulate together through the entire system. The concentration of oil in circulation depends on the initial charge of oil, the characteristics of the compressor in retaining oil therein, the compressor speed, and the refrigerant flow conditions. Normally, the amount of oil circulation in the system is directly proportional to compressor speed and inversely proportional to flow rate of the refrigerant.

Too much oil in the system impedes the cooling effect of the refrigerant and the above-described relationships regarding oil circulation in the system are in conflict with optimized efficiency of operation.

The specific type of rotary compressor to which this invention will be related in a preferred embodiment is disclosed in US. Pat. No. 3,552,886, to John W. Olson, .Ir., issued Jan. 5, I97l, which disclosure is incorporated by reference herein.

In such rotary compressors, oil enters the rotor casing during the compression stroke of each piston because of normal blow-by of the oil past the piston rings.

Oil can leave the rotor case in two primary ways.

First, at some point in the suction stroke of each piston, v

the pressure in the rotor case is momentarily greater than that on the top side of the piston, the latter being in the process of filling up its associated cylinder with a charge of refrigerant/oil mixture from the system. Accordingly, a reverse blow-by is achieved from the rotor case into the cylinder and subsequently pumped out into the system by the scouring action of the piston rings. Second, blow-by equalizing holes are normally provided in an attempt to equalize the rotor case and suction pressures, by connecting the rotor case to the suction side of the compressor. Oil thus escapes from the rotor case through these equalizing holes whenever a pressure differential exists from the rotor case to the suction side of the compressor.

It is an object of the present invention to provide a new and novel rotary refrigerant compressor and lubrication system therefor.

Another object of the present invention is to provide a new and novel rotary refrigerant compressor and lubrication system therefor, wherein said lubrication system utilizes the inherent oil flow patterns in such rotary compressors to enhance the lubricating and cooling functions of the compressor and its associated systems.

Yet another object of the present invention is to provide a new and novel blow-by lubricating system for rotary piston refrigerant compressors wherein the amount of oil present is constrained to an optimum level in the rotor case and minimized in the balance of an associated refrigerating system.

These and other objects of the present invention will become more fully apparent with reference to the following specification and drawings which relate to a preferred embodiment of the invention.

In the drawings:

FIG. 1 is an end view of a compressor of the present invention illustrating the drive shaft and adjacent oil porting;

FIG. 2A is a cross-section taken along line 2A-2A of FIG. 1 illustrating the internal structure and oil flow patterns of the present invention;

FIG. 2B is a partial cross-section taken along line 2B2B of FIG. 1; and

FIG. 3 is an end view of the opposite end of the compressor from that of FIG. 1.

Referring in detail to the drawings. the compressor 10 of the present invention is shown as including a one piece. substantially cylindrical cylinder block and rotor case assembly 12, having a cylinder block 12A in one end thereof and a hollow housing portion 12B at the other.

The hollow portion 12B mounts a front cover plate 14 by means of a plurality of cap screws 14A and by means of a plurality of bolts 15, the cylinder block 12A mounts a cylinder head 16 and a valve plate 18 to com plete a closed housing assembly for the compressor 10.

The front housing plate 14 covers one open end of the assembly 12 while the cylinder head 16 and the valve seat plate 18, the latter positioned substantially coextensively with the interior of the former, cover the other open end of the assembly I2.

The interior of the assembly 12 comprises an oil sump or reservoir 20 and serves further as a rotor case for the input rotor or swash plate 22 and its cooperating wobble or planet plate 24 which serve to drive pistons 26 in the cylinders 28 in the cylinder block portion 12 of the assembly 12 in the manner "fully described in the herein referenced Pat. No. 3,552,886.

The pistons 26 cooperate with conventional reed or vane type suction valves (not shown) in a suction valve plate 30 juxtaposed between the assembly 12 and the valve seat plate 18, the latter being ported-to respectively connect the cylinders 28 with peripherally disposed suction or input chambers 16A in the cylinder head 16 on the respective suction strokes of the pistons 26. All of the suction chambers 16A are in open communication with the refrigeranvoil input (suction) coupling 168 on the cylinder head 16 by means of appropriate conventional porting (not shown).

The cylinders 28 are selectively connected through respective conventional open ports in the suction valve plate and valve seat plate 18, on respective compression strokes of the pistons 26, with a centrally disposed output or discharge chamber 16C within the cylinder head 16 through conventional vane or reed type discharge valves 32, schematically shown in FIG. 2A.

The discharge chamber 16C is directly connected to a discharge coupling 16D on the exterior of the cylinder head 16.

As is now known in the art, the planet plate 24 nutates upon a fixed bevel gear assembly 34 mounted centrally within the oil sump 20 on the assembly 12, substantially symmetrical with the central axes of all of the cylinders 28 therein.

The rotor 22 is keyed for rotation to an input drive shaft 36, substantially coaxial with the fixed bevel gear assembly 34, rotor 22 and planet plate 24, the said drive shaft 36 being journalled in a first needle bearing assembly 38 housed within the front housing plate 14. The front housing plate 14 also includes a shaft housing 148 which defines a shaft seal cavity 40 housing a shaft seal 42, both concentrically disposed about the drive shaft 36.

A first lubricating gap 44 is provided between the rotor 22 and the interior of front housing plate 14, about the drive shaft 36 by means of a first thrust bearing assembly 46 therebetween; illustrated as being of the roller or needle bearing type.

A second lubricating gap 48 is provided between the rotor 22 and the planet plate 24 by means of a second thrust bearing assembly 50 therebetween, illustrated as being of the roller or needle bearing type.

An axial lubricating port 52 is provided in the drive shaft 22 and is connected by intersecting radial cross ports 54 in said shaft to the shaft seal chamber 40 in the front housing plate 14.

The axial port 52 extends inwardly from the radial cross ports 54 into communication with the second lubricating gap 48 intermediate the rotor 22 and planet plate 24, thus establishing a first path for the flow of oil from the sump 20 through the said second thrust bearing assembly 50, second gap 48, the said axial port 52 and radial cross-ports 54 into the shaft seal cavity 40.

Furthermore, a second path for the flow of oil exists from the sump 20, through the first thrust bearing assembly 46, first gap 44 and journal bearing 38 into the shaft seal cavity 40.

A third path for the flow of oil is established by a substantially radial flow port 56 in the front housing plate 14 extending from the shaft seal cavity 40 into intersecting communication with a port 58 in the peripheral shell of the assembly 12 which communicates directly through the valve seat plate 18 with the suction chambers 16A in the cylinder head 16 to complete the third path for the flow of oil from the input shaft seal cavity 40 to the said suction chambers 16A. The radial flow port 56 is closed at its outer end by a closure plug 56A.

Referring now to FIG. 28, a fourth path for the flow of oil is provided by means of a second. longitudinal flow port 60 in the peripheral shell of the assembly 12 which extends directly from the rotor case and oil sump 20 to one of the suction chambers 16A in the cylinder head 16. A dumper orifice 60A is provided in the suction chamber adjacent the end of the second flow port 60 and comprises a calibrated flow restrictor therein to permit sufficient oil to pass from the sump 20 into the suction chambers 16A at relatively high compressor speeds of rotation to preclude overheating of the compressor 10. This overheating is caused by the efficient centrifugal scouring of oil from the rotating parts of the compressor 10, causing such a build up of oil in the sump 20 that the oil physically interferes with the moving parts of the compressor 10. As a result, fluid friction between the moving parts and the oil in the sump 20 will cause overheating of the compressor at speeds, for example, on the order of 5000 r.p.m.

By means of the calibrated dumper orifice 60A, sufficient oil will by by-passed from the sump to the suction chambers 16A via the second flow port 60 to preclude the occurrence of an excess (interfering) oil level in the sump and rotor case 20 at such high compressor speeds.

A return path for oil from the suction chambers 16A .is through the cylinders 28 by the well known phenomenon of blow-by past the pistons 26 (and their piston ring assemblies. not shown) onto the planet plate 24 and bevel gear assembly 34, from whence this oil will flow downward into the sump 20.

Operation Assuming rotation of the input or drive shaft 36 of the compressor 10, and with particular reference to FIGS. 1 and 2, the operation of the present invention is as follows:

Oil and refrigerant are drawn into the cylinders 28 from suction chambers 16A by the pistons 26 during the suction stroke thereof. The charge of oil and refrigerant are compressed in the cylinders 28 and discharged into the discharge chamber 16C. During the compression stroke of the pistons 26 and the cylinders 28, oil is scraped off the walls of the cylinders 28 and returns to the oil sump or rotor case 20 as part of the blow-by that occurs past the rings (not shown) and the ring gaps (not shown) of the pistons 26 which are conventionally known.

The blow-by gas and a small quantity of oil is made to leave the sump 20 via the first and second paths of oil flow described above.

To recapitulate, the first flow path for lubricating oil mixed with refrigerant gas is from the sump 20 through the first thrust bearing assembly 46, first lubricating gap 44, journal bearing assembly 38 and into the shaft seal cavity 40, thus lubricating both the first thrust bearing assembly 46 and the journal bearing assembly 38.

The second lubricating path achieved is from the sump 20 through the second thrust bearing assembly 50, second lubricating gap 48, axial port 52 in the drive shaft 22, radial cross ports 54 in the drive shaft 22, and thence into the shaft seal cavity 40. Therefore, the thrust bearing assembly 50 is adequately lubricated.

Gas and oil flowing through the shaft seal cavity 40 cools and lubricates the shaft seal 42 as well.

Thereafter. gas and oil leave the shaft seal cavity 40 via the radial port 56 in the front housing plate 14 and thence pass through the axially disposed tube 58 in the assembly 12 to the suction chambers 16A.

Thereafter, on an intake or suction stroke of the pistons 26 and the cylinders 28 this gas and oil mixture mixes with the incoming charge of refrigerant in the suction chambers 16A and thence is drawn into the cylinders 28 and a portion of the oil which escapes the cylinders 28 via the blow-by action is thus recycled within the compressor 10 through the said cylinders.

It can now be readily seen that this method of lubrication traps an adequate quantity of oil in the sump 20, where the action of the rotating-oscillating mechanism comprising the rotor 22 and wobble or planet plate 24 causes the other components of the compressor 10, which are in need of lubrication, to be splashlubricated adequately. The reason that this system traps oil is that in order for the refrigerant gas to escape through the lubricating paths described above, it must first get past the first and second thrust bearing assemblies 46 and 50, respectively, which are in rotation and also which come in contact with the surface of the rotor 22 which is itself in rotation.

Therefore, some particles of oil trying to enter the passages or lubricating gaps 44 and 48 between the foregoing elements are slung back into the rotor case or sump 20 through the action of centrifugal force imparted by the needle bearings in the thrust bearing assemblies 44 and 46 as well as the surface of the rotor 22. Notwithstanding this conservation of the oil in the sump 20, a small quantity of oil remains entrained in the refrigerant gas which is adequate for lubrication and does escape through the drive shaft 22 and shaft seal cavity 40 to be recycled into the suction chambers 16A as previously described.

As the speed of rotation of the rotor 22 and its related parts increases, the level of the oil in the sump 20 is precluded from increasing beyond a proper optimized level for cool running of the compressor by the escape of excess oil from the sump 20, through the second flow port 60 and the calibrated dumper orifice 60A into the suction chambers 16A, from whence a portion thereof is recycled.

As can be readily seen from the foregoing specification and drawings the present invention provides a new and novel oil lubrication system for refrigerant compressors wherein the lubricating oil and refrigerant are mixed, and wherein the amount of oil in circulation in the oil sump of the compressor is constrained to a proper level and the amount of oil in circulation in the system with the refrigerant gas is minimized. Therefore, the compressor of the present invention provides maximum lubrication and maximum cooling efficiency which, heretofore, have been incongruous joint characteristics in the art.

What is claimed:

1. In a refrigerant compressor utilizing refrigerant entrained oil for lubrication and having a plurality of pistons reciprocated by means of a wobble plate means driven by an input rotor means and an input shaft means connected with said rotor means;

a housing for said compressor including a cylinder block for said pistons, and a sump chamber adjacent said cylinder block housing said wobble plate and said input rotor;

a first end plate means on said housing including journal bearing means, a shaft seal cavity and shaft seal means providing mounting and entry means for said input shaft adjacent said sump;

a second end plate means at the opposite end of said housing including refrigerant suction and discharge chambers and valve means selectively interconnecting the same with said cylinder block; and

a recirculating blow-by lubrication system comprising:

a. first flow port means extending from said shaft seal chamber in said first end plate means to said suction chamber in said second end plate means;

b. first peripheral bearing means between said input rotor means and said first end plate means effecting a first predetermined oil flow gap between said rotor means and said first end plate means, said first oil flow gap establishing communication for said refrigerant entrained oil from said sump to said journal bearing means and through the latter to said shaft seal cavity;

c. second peripheral bearing means between said input rotor means and said wobble plate means effecting a second predetermined oil flow gap between said rotor means and said wobble plate means. establishing communication from said sump to the base of said input shaft;

(1. second flow port means in said input shaft ex-' tending from said second oil flow gap to said shaft seal chamber; and

e. a return flow path for said refrigerant entrained oil from said suction chamber to said sump comprising conventional blow-by of said oil through said cylinder block.

2. The invention defined in claim 1, wherein said first peripheral bearing means comprises a needle bearing assembly in mutual engagement with said input rotor means and said end plate means. I

3. The invention defined in claim 1, wherein said first peripheral bearing means comprises a needle bearing assembly in mutual engagement with said input rotor means and said end plate means; and wherein said journal bearing means comprises a needle bearing assembly about the periphery of said input shaft means. in said first end plate means, intermediate said first oil flow gap and said shaft seal cavity.

4. The invention defined in claim 2, wherein said second peripheral bearing means comprises a needle bearing assembly in mutual engagement with said input rotor means and said wobble plate means about the periphery of said base of said input shaft and said second flow port means.

5. The invention defined in claim 1, wherein said first flow port means comprises first flow passage means in said first end plate extending from said shaft seal chamher to the outer wall of said housing and second flow passage means, in registry with said first flow passage means, extending through said outer wall of said housing to said input chamber.

6. The invention defined in claim 1, wherein said first peripheral bearing means comprises a needle bearing assembly in mutual engagement with said input rotor means and said end plate means; and wherein said sec ond peripheral bearing means comprises a needle bearing assembly in mutual engagement with said input rotor means and said wobble plate means about the periphery of said base of said input shaft and said second flow port means.

7. The invention defined in claim 1, wherein said first peripheral bearing means comprises a needle bearing assembly in mutual engagement with said input rotor means and said end plate means; wherein said journal bearing means comprises a needle bearing assembly about the periphery of said input shaft means, in said first end plate means, intermediate said first oil flow gap and said shaft seal cavity; and wherein said second peripheral bearing means comprises a needle bearing assembly in mutual engagement with said input rotor means and said wobble plate means about the periph ery of said base of said input shaft and said second flow port means.

8. The invention defined in claim 1, wherein said first peripheral bearing means comprises a needle bearing assembly in mutual engagement with said input rotor means and said end plate means; and wherein said second peripheral bearing means comprises a needle bearing assembly in mutual engagement with said input rotor means and said wobble plate means about the periphery of said base of said input shaft and said second flow port means; and wherein said first flow port means comprises first flow passage means in said first end plate extending from the shaft seal chamber to the outer wall of said housing and second flow passage means, in registry with said first flow passage means, extending through said outer wall of said housing to said input chamber.

9. The invention defined in claim 1. wherein said first peripheral bearing means comprises a needle bearing assembly in mutual engagement with said input rotor means and said end plate means; wherein said journal bearing means comprises a needle bearing assembly about the periphery of said input shaft means. in said first end plate means, intermediate said first oil flow gap and said shaft seal cavity; wherein said second peripheral bearing means comprises a needle bearing assembly in mutual engagement with said input rotor means and said wobble plate means about the periphery of said base of said input shaft and said second flow port means; and wherein said first flow port means comprises first flow passage means in said first end plate extending from said shaft seal chamber to the outer wall of said housing and second flow passage means, in registry with said first flow passage means, extending through said outer wall of said housing to said input chamber.

10. ln a refrigerant compressor utilizing refrigerant entrained oil for lubrication and having a plurality of pistons reciprocated by means of a wobble plate means driven by an input rotor means and an input shaft means connected with said rotor means;

a housing for said compressor including a cylinder block defining respective cylinders for said pistons, and a sump chamber adjacent said cylinder block housing said wobble plate and said input rotor;

a first end plate means on said housing including journal bearing means, a shaft seal cavity and shaft seal means providing mounting and entry means for said input shaft adjacent said sump chamber;

a second end plate means at the opposite end of said housing including refrigerant suction and discharge chambers and valve means selectively interconnecting the same with said cylinder block; and

a recirculating blow-by lubrication system comprising means defining first and second oil flow paths from said sump between said rotor means and said first end plate means and between said rotor means and said wobble plate means, respectively, into said shaft seal cavity, a third flow path from said shaft seal cavity to said input chamber and a fourth flow path from said suction chamber through said cylinders to said sump chamber.

11. The invention defined in claim 10, wherein said lubrication system further includes a fifth oil flow path from said sump chamber through calibrated flow restricting means to said suction chamber, said flow restricting means being calibrated to limit the quantity of oil in said sump chamber to a predetermined maximum.

12. In a refrigerant compressor utilizing refrigerant entrained oil for lubrication and having a plurality of pistons reciprocated by means of a wobble plate means driven by an input rotor means and an input shaft means connected with said rotor means;

a housing for said compressor including a cylinder block for said pistons, and a sump chamber adjacent said cylinder block housing said wobble plate and said input rotor, said pistons being reciprocated in cylinders adjacent said sump, said cylinders being in open communication with said sump chamber; and

refrigerant suction and discharge chambers selectively communicating with said cylinders:

a blow-by lubrication system comprising circulating means effecting circulation of entrained oil from said sump. over said wobble plate, said rotor means and said input shaft means. thence to said refrigerant suction chamber and back through said cylinders into said sump chamber;

said circulating means acting continuously during operation of said compressor to centrifugally extract a substantial portion of said entrained oil from said refrigerant and to entrap said extracted oil in said sump.

13. The invention defined in claim 12, wherein said blow-by lubrication system further includes calibrated oil by-pass means interconnecting said sump chamber and said suction chamber limiting the amount of oil in said sump chamber to a predetermined maximum.

14. In a refrigerant compressor utilizing refrigerant entrained oil for lubrication and having a plurality of pistons reciprocated by means of a wobble plate means driven by an input rotor means and an input shaft means connected with said rotor means;

a housing for said compressor including a cylinder block for said pistons, and a sump chamber adjacent said cylinder block housing said wobble plate and said input rotor;

a first end plate means on said housing including journal bearing means, a shaft seal cavity and shaft seal means providing mounting and entry means for said input shaft adjacent said sump;

a second end plate means at the opposite end of said housing including refrigerant suction and discharge chambers and valve means selectively interconnecting the same with said cylinder block; and

a recirculating blow-by lubrication system comprising:

a. first flow port means extending from said shaft seal chamber in said first end plate means to said suction chamber in said second end plate means;

b. first peripheral bearing means between said input rotor means and said first end plate means effecting a first predetermined oil flow gap be tween said rotor means and said first end plate means, said first oil flow gap establishing communication for said refrigerant entrained oil from said sump to said journal bearing means and through the latter to said shaft seal cavity;

0. second peripheral bearing means between said input rotor means and said wobble plate means effecting a second predetermined oil flow gap between said rotor means and said wobble plate means, establishing communication from said sump to the base of said input shaft;

d. second flow port means in said input shaft extending from said second oil flow gap to said shaft seal chamber;

e. a return flow path for said refrigerant entrained oil from said suction chamber to said sump comprising conventional blow-by of said oil through said cylinder block; and

f. calibrated flow means interconnecting said sump chamber and said suction chamber, limiting the quantity of oil in said sump chamber to a predetermined maximum.

15. The invention defined in claim M, wherein said first peripheral bearing means comprises a needle bearing assembly in mutual engagement with said input rotor means and said end plate means.

16. The invention defined in claim 14, wherein said first peripheral bearing means comprises a needle bearing assembly in mutual engagement with said input rotor means and said end plate means; and wherein said journal bearing means comprises a needle bearing assembly about the periphery of said input shaft means, in said first end plate means, intermediate said first oil flow gap and said shaft seal cavity.

17. The invention defined in claim 14 wherein said second peripheral bearing means comprises a needle bearing assembly in mutual engagement with said input rotor means and said wobble plate means about the periphery of said base of said input shaft and said second flow port means.

18. The invention defined in claim 14, wherein said first flow port means comprises first flow passage means in said first end plate extending from said shaft seal chamber to the outer wall of said housing and second flow passage means, in registry with said first flow passage means, extending through said outer wall of said housing to said input chamber.

19. The invention defined in claim 14, wherein said first peripheral bearing means comprises a needle bearing assembly in mutual engagement with said input rotor means and said end plate means; and wherein said second peripheral bearing means comprises a needle bearing assembly in mutual engagement with said input rotor means and said wobble plate means about the periphery of said base of said input shaft and said second flow port means.

20. The invention defined in claim 14, wherein said first peripheral bearing means comprises a needle bearing assembly in mutual engagement with said input rotor means and said end plate means; wherein said journal bearing means comprises a needle hearing as sembly about the periphery of said input shaft means, in said first end plate means, intermediate said first oil flow gap and said shaft seal cavity; and wherein said second peripheral bearing means comprises a needle bearing assembly in mutual engagement with said input rotor means and said wobble plate means about the periphery of said base of said input shaft and said second flow port means.

21. The invention defined in claim 14, wherein said first peripheral bearing means comprises a needle hearing assembly in mutual engagement with said input rotor means and said end plate means; and wherein said second peripheral bearing means comprises a needle bearing assembly in mutual engagement with said input rotor means and said wobble plate means about the periphery of said base of said input shaft and said second flow port means; and wherein said first flow port means comprises first flow passage means in said first end .plate extending from said shaft seal chamber to the outer wall of said housing and second flow passage means, in registry with said first flow passage means, extending through said outer wall of said housing to said input chamber.

22. The invention defined in claim 14, wherein said first peripheral bearing means comprises a needle bearing assembly in mutual engagement with said input rotor means and said end plate means; wherein said journal bearing means comprises a needle bearing assembly about the periphery of said input shaft means, in said first end plate means, intermediate said first oil flow gap and said shaft seal cavity; wherein said second peripheral bearing means comprises a needle bearing assembly in mutual engagement with said input rotor means and said wobble plate means about the periphery of said base of said input shaft and said second flow port means; and wherein said first flow port means comprises first flow passage means in said first end plate extending from said shaft seal chamber to the outer wall of said housing and second flow passage means, in registry with said first flow passage means, extending through said outer wall of said housing to said input chamber.

23. The invention defined in claim 14, wherein said calibrated flow means comprises third flow port means having in line flow restricting means therein in direct communication from said pump to said suction cham her, said flow restricting means constraining the flow of oil and refrigerant gas through said third flow means as a function of the rotational speed of said input rotor means.

24. In a compressor having a rotor case,

including an oil sump,

a rotor and other moving parts in said casing, the rotor centrifugally ejecting oil therefrom in said rotor casing,

suction and discharge chambers for the compressor,

means introducing oil-bearing gas from an inlet chamber into said casing to lubricate the moving parts, said means producing a high pressure in the casing above that of the inlet chamber,

first oil flow passage means from the casing radially inwardly of the rotor and in contact therewith, thence to the inlet chamber, thereby being subject to centrifugal force that separates oil from the gas in the casing that may collect in the sump, and rise into excessive contact with the moving parts;

means limiting the amount of oil in said sump and said rotor casing to a predetermined maximum precluding over-heating of said compressor at high rotor speeds from physical interaction of the moving parts with said oil,

said means comprising a second, calibrated flow pas sage means directly interconnecting said rotor case with said suction chamber,

said second flow passage means being located in the casing to receive oil from the sump picked up by the rotor and flung out by its rotary motion, and being subjected to the pressure difference between the casing and the inlet, thereby returning oil to the inlet chamber and preventing excessive accumulation in the sump.

25. In a refrigerant compressor utilizing refrigerant entrained oil for lubrication and having drive means including a drive shaft, a cylinder block being formed with a plurality of cylinders arranged substantially in a circle, a cylinder head formed with a refrigerant suction and discharge chamber, valve means for supplying fluid to said compressor through said suction chamber and discharging said fluid through :said discharge chamber, wobble plate means, said wobble plate means being activated to oscillate by a rotating swash plate means carried by the said drive shaft of the drive means, a pair of facing bevel gear means, one bevel gear means being carried by said wobble plate and the second bevel gear means being in fixed relationship to said cylinder block to prevent rotation of said wobble plate, bearing means to support the wobble plate and to hold the same against radial and axial displacement while permitting its wobbling movement, and connecting rods and respective piston means for each rod mounted to be reciprocated by said wobble plate in each one of said respective cylinders, the improvement comprising:

a housing for said compressor including a sump chamber adjacent said cylinder block for housing said wobble plate means, said rotating swash plate, said bevel gear means, and said drive means. said cylinders of said cylinder block being in open communication with said sump chamber;

a blow-by lubrication system including circulating means effecting circulation of oil from said sump. over said wobble plate means, said rotating swash plate means. said bevel gear means, and said drive means, thence to said refrigerant suction chamber and back through said cylinders into said sump chamber;

said circulating means acting continuously during op- I said sump chamber to a predetermined maximum.

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GB304555A * Title not available
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Classifications
U.S. Classification417/269, 417/439
International ClassificationF04B27/10, F25B31/00
Cooperative ClassificationF25B31/00, F04B27/1036, F04B27/109, F25B31/002
European ClassificationF25B31/00B, F25B31/00, F04B27/10C8, F04B27/10C