US3784331A - Radial compressor with two-piece cylinder housing and shell - Google Patents

Radial compressor with two-piece cylinder housing and shell Download PDF

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US3784331A
US3784331A US00254511A US3784331DA US3784331A US 3784331 A US3784331 A US 3784331A US 00254511 A US00254511 A US 00254511A US 3784331D A US3784331D A US 3784331DA US 3784331 A US3784331 A US 3784331A
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shaft
cylinder housing
housing
bores
cross bores
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US00254511A
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J Heidorn
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Motors Liquidation Co
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Motors Liquidation Co
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement

Definitions

  • Front and rear cylinder walls support [56] References Cited a circumferentially located sheet metal shell sealed to UNITED STATES PATENTS form a continuously circumferential high pressure dis- 3 695 786 10 1972 Gannaway 417/273 charge space with enlarged dischmge cavities- 3:008:628 11/1961 Gerteis 417 419 A Short Shaft and bearing assembly is formed between 2,752,088 6/1956 Bogerd et a1. 417/567 the front and rear walls to reduce compressor length. 2,893,626 7/1959 Weibel 417/419 The sheet metal shell and cylinder housing form a 3,174,436 3/1965 Wanner.... 1.
  • Automotive refrigeration systems typically have the component parts thereof located within a limited space inside the engine compartment of a vehicle. It is desirable that the refrigeration compressor have a substantial capacity without occupying too much of the engine compartment space of a vehicle.
  • One method to accomplish this purpose is to reduce the front to rear dimensions of refrigerant compressors for the use in vehicles.
  • One well known type of pump which has a reduced front to rear dimensional configuration is the type of pump or compressor which includes a plurality of radial cylinder bores each including a piston reciprocated with respect to the bores for compressing and discharging gas.
  • each of the cylinders are located in a common plane to reduce the front to rear di mension of the compressor.
  • An object of the present invention is to improve a compressor having radially located across bores therein, each with a reciprocating piston for compressing gas by the provision of an improved short shaft configuration within the compressor having main bearings located close to crank arm loads to reduce shaft movements.
  • Still another object of the present invention is to provide an improved high capacity compressor with a large discharge volume therein formed by a sheet metal shell having surface portions thereon sealingly engaged with continuous annular seals in a rigid cylinder bore housing including a rear wall and a front wall forming the front and rear of the large discharge volume in the compressor and wherein the cylinder housing includes a central suction cavity completely circumferentially surrounded by a large volume discharge space to muffle compressor noise.
  • Still another object of the present invention is to provide an improved compact high capacity compressor for use in automotive air conditioning systems includ ing a rigid cylinder housing having cross bores therein supporting a metal shell which includes a conical surface on one end thereof in which is located a rigid bearing housing, a conical surface locating the first bearing in alignment with a second bearing on a rigid wall of the cylinder housing to align shaft end portions for rotation with respect to said cylinder housing.
  • FIG. 1 is a view in vertical section through a compressor including the present invention
  • FIG. 2 is a fragmentary view in horizontal section taken along the line 2--2 of FIG. I looking in the direction of the arrows;
  • FIG. 3 is a vertical sectional view taken along the line 3-3 of FlG. 1 looking in the direction of the arrows;
  • FIG. 4 is a fragmentary sectional view taken along the line 4-4 of FIG. I. looking in the direction of the arrows;
  • FIG. 5 is an end elevational view of the cylinder housing of the compressor in FIG. I;
  • FIG. 6 is a fragmentary sectional view taken along the line 6-6 of FIG. 5;
  • FIG. 7 is a fragmentary sectional view taken along the line 7--7 of FIG. 5.
  • FIG. 1 a compressor 10 is illustrated. It includes a rigid cast cylinder housing 12 having radially located cross bores 14, 16 on one axis of the cylinder housing. A second pair of cross bores 18, 20 are formed on a second axis of the housing 12 at a right angular or cross relationship to the bores l4, 16 as is best seen in FIG. 3.
  • the cylinder housing 12 has a circular configuration as seen in FIG. 5 which is intersected by the cross bores.
  • the circular configuration and the cross bore arrangement produces an extremely compact planar configuration of the compressor as viewed in end elevation.
  • the housing includes a rear wall 22. It has an outwardly directed central boss 24 thereon surrounded by a concentric stepped wall segment 25 integrally joined with a radially outwardly located, bore forming, thin sectioned wall segment 26 having an enlarged peripheral flange 28 thereon.
  • An inclined surface 30 on the outer face of the flange 28 is inclined inwardly of the rear wall 22 continuously therearound. It defines a clamp surface located in interlocking relationship with the bent end 32 of an outer sheet metal shell 34.
  • One feature of the present invention is that the cylinder housing 12 and the outer sheet metal shell 34 form a two-piece construction which is easily assembled to form an unusually compact suction cavity and discharge chamber and muffler cavity configuration located between the rear wall 22 of the housing and a front wall 36 thereon which has an enlarged peripheral flange 38 thereon with a front bearing face 40.
  • the peripheral flange 38 is formed continuously around the front edge of the housing 12.
  • the front wall 36 is circular and has a radially inwardly directed edge thereon forming a central opening 42 in the wall through which a short shaft drive mechanism 44 fits.
  • the drive mechanism 44 more particularly is located interiorly of the cylinder housing within a low pressure suction space or cavity 46 therein.
  • the suction cavity 46 communicates with a suction port 48 formed through an inclined boss 50 extending outwardly ofthe rear wall 22 at an angle to communicate with a side cutout portion of the suction cavity 46 in the housing 12 as is best seen in FIG. 7.
  • a suction screen 52 having an elongated conical configuration has a head portion 54 thereon seated in the port 48 for removing particles from return gas passing into the compressor during its operation.
  • the rear wall 22 includes a discharge port 56 which isformed in an outwardly angularly inclined boss 58 on the outer surface of the end wall 22.
  • Port 56 is in intersecting relationship with one end of a passageway 60 which has the opposite end thereof in communication with a portion of an annular high pressure cavity 62 formed between the outer shell 34 and the outer periphery of the cylinder housing 12.
  • the inclined configuration of boss 50 and boss 58 reduces the length of space required for mounting the compressor and connecting it to hoses in the refrigerant system.
  • the housing 12 in addition to the rear wall 22 and the front wall 36 includes circumferentially spaced cut out walls 64 therein which form a muffler cavity 66 between each of the cross bores in the housing 12.
  • Each of the cavities 66 serve to muffle high pressure gas discharged from the cross bores during compressor operation.
  • Each cut out wall 64 includes a base segment 68 which is in heat exchange relationship with cool return gas from the suction port 48. Additionally, the cavities 66 are located closely circumferentially adjacent an upper narrow opening 70 between the housing 12 and shell 34 communicating each of the cross bores with the cavity 62.
  • the suction cavity 46 and the annular high pressure cavity 62 are sealed apart from one another between the two pieces made up by the cylinder housing 12 and the outer shell 34. More particularly, as illustrated in FIGS. 1 and 2, the shell 34 includes a circular peripheral wall 72 having an inner surface stepped at 74 and at 76.
  • the stepped portion 74 is a continuous circumferential surface which is in sealing engagement with an O-ring seal 77 circumferentially located continuously within a circular groove 78 in the outer periphery of the flange 28 completely therearound.
  • the stepped portion 76 locates the outer shell 34 against the radially outer peripheral edge of the flange 38.
  • the shell includes a radially inwardly bent segment 80 thereon formed continuously around the front outer periphery of the shell. It has an inner surface 82 thereon which is located in sealing engagement with an O-ring seal 84 formed continuously circumferentially around the front bearing face 40 on the front wall 36.
  • the bent edge 32 on the shell is spun over against the surface 30 so as to cause the shell surface 82 to be drawn into sealing engagement with the O-ring seal 84 and to force the stepped portion 74 into sealing engagement with the O-ring seal 77.
  • the inclination on the support surface 30 and the spun over edge 32 cooperate to produce a clamped interconnection between the two pieces constituted by the housing 12 and the shell 34 to resist pressure forces in the high pressure cavity 62 tending to cause these parts to separate radially with respect to one another.
  • the spun over edge 32 and the inner surface 82 are drawn together so as to produce a peripheral force on each of the cross bores at the radially outermost ends thereof.
  • a rigid member or shell reinforcing retainer or plate 86 is located in seated relationship in a counterbore 87 in each of the bores.
  • the reinforcing retainer disc 86 has the peripheral edge thereof located in juxtaposed relationship withthe inside surface of each of the bores at the bearing point between the inner surface 82 on the outer shell and the front bearing face 40 thereon.
  • the retainer reinforces the stepped wall segment 26 of the housing which forms the opposite wall of each of the bores. It also serves to reinforce the cut out walls 64.
  • the retainer disc 86 as best seen in FIGS. 2 and 3, includes a pair of spaced holes 88, 90 therein which communicates each of the cross bores with a valve cage opening 92 located between the disc and the outer shell 72.
  • the arrangement eliminates the need for drilling several small holes to produce adequate discharge flow area.
  • the disc serves as a support for an improved low cost discharge valve assembly 93 which includes parts made of sheet metal stock formed to produce selective opening and closing of the discharge valve openings 88, 90 in the disc during compressor operation.
  • valve assembly 93 includes an elongated rectangularly shaped reed element 94 having a free end portion 96 thereon movable with respect to a guide slot 97 formed on one side of a dome valve retainer 98.
  • the dome valve retainer 98 includes a plurality of circumferentially spaced cut out portions 100 in the edge thereof between a plurality of radially outwardly directed fingers 102 which are press fit within the counterbore 87 to hold the disc 86 in place therein.
  • Each of the cut outs 100 serve to communicate the valve cage opening 92 with the peripheral opening 70 between each of the bores and the outer shell 34.
  • the dome has the top portion 104 thereon in engagement with the inner surface of the peripheral wall 72 to maintain a radially inwardly directed bias on the dome so as to firmly spring bias the fingers 102 into the counterbore and to allow some flexing for changes in heat and pressure.
  • valve assembly 93 includes a rectangularly configured back-up plate 106 which has a distal end 108 thereon located within the dome slot 97 to overlie the free end 96 of the reed element 94.
  • - distal end 108 is supported by the dome in this position and will serve to limit outward movement of the reed away from the openings through the disc during a compression stroke.
  • the dome 98 further includes a downwardly struck tab portion 109 thereon which is directed through fixed ends of the back-up plate 106 and the valve 94 and into interlocked relationship with a slot 111 in one side of the disc 86 thereby to firmly secure the fixed end of both the retainer plate and the valve with respect thereto.
  • Each of the cross bores supports a piston with an elongated skirt portion 112 slidably supported on the inner surface of the bore for reciprocation with respect thereto.
  • the skirt 112 surrounds an elongated piston stem 114 which includes a flat surface 116 thereon supported by a sliding reciprocating surface 118 ofa slider block 120 on the short shaft drive mechanism 44.
  • the mechanism 44 is configured to reduce bending moments on a compressor drive shaft by being configured to locate main shaft bearings in close axial relationship with the primary loads on the shaft.
  • the mechanism 44 includes a drive shaft 122 with an outboard exten-sion 124 thereon adapted to be connected to a rotary drive source.
  • the shaft 122 includes an inboard shaft journal 126 supportingly received by a main needle bearing 128 located in a bearing bore 130 formed in a tubular extension 132 in line with the central boss 24 on the rear wall 22 and directed axially inwardly thereof.
  • the journal 126 is supported substantially throughout its length by the main bearing 128 and a thrust washer 134 which fits over the shaft journal 126 to engage the end of the tubular extension 132.
  • a shaft eccentric portion 136 is joined to the shaft journal 126 by an intermediate shaft portion 138 of a short length and having an inclination with respect to the axis of the shaft through the extension 124 and the journal 126.
  • the shaft includes a second inclined portion 140 joining the eccentric 136 to a sec ond shaft journal portion 142 which is supported by a second main bearing 144.
  • the main bearing 144 for the shaft journal 142 is supported on the outer shell 34.
  • the outer shell constitutes a sheet metal bearing support to align the bearing supported shaft portions during compressor operation.
  • the outboard bearing support for the shaft portion 132 is constituted by a conically configured axial extension 145 formed integrally with the bent segment 80 of the shell 34. It includes a radially inwardly directed support surface 146 arranged generally perpendicularly with respect to the axis of the drive shaft 122.
  • the support surface 146 has an opening 148 located centrally thereof directed therethrough in which is located an inward tubular portion 150 of a rigid bearing and seal housing 152.
  • the housing 152 is connected to the surface 146 by means of a weld 154.
  • the tubular extension 150 includes a bearing bore 156 therein in which is located the second main bearing 144 having needles 158 to rotatably support the shaft journal portion 142.
  • the housing 152 is closely aligned to locate the bore 156 coaxially of the bore 130 whereby the shaftjournal portions 126, 142 are supported on the main bearings in accurate axial alignment with one another.
  • the mechanism 44 has a short shaft with the main bearings closely adjacent the shaft eccentric 136 thereby to reduce the distance between the main forces on the shaft eccentric and the main bearing points to reduce shaft moments.
  • the rigid housing 152 is supported by the conical extension 145 on the outer shell 34 to produce a controlled amount of flexure to assure alignment of the bores 130, 156.
  • the housing 152 includes a large diameter bore 160 in which is located a rotary shaft seal assembly 162.
  • the shaft seal is of a conventional type including a seal ring 164 fixed by means of a retainer ring 166 within a counterbore in the housing 152.
  • the ring 164 is sealed by means of an O-ring seal 168 at the outer periphery thereof. it includes an axially inwardly locatedface 170 in sliding sealing engagement with the face 172 of a rotary seal 174 carried by a conical spring 176 and bracket 178 secured on the shaft 122 for rotation therewith.
  • the seal housing 152 along with the seal assembly 162 therein will seal the shaft against leakage of gas from the low pressure suction cavity 46.
  • the improved short shaft mechanism 44 includes an arrangement for locating balanced weights within the short axial limits between the inner and outer walls of the cylindrical housing 12.
  • the inclined intermediate shaft portion 138 includes a flat end surface 180 against which the base 182 ofa counterweight 184 is located.
  • the counterweight 184 has radially outwardly directed segments 186 thereon located around the outer periphery of the tubular extension 132 for rotation therearound.
  • a screw 188 fixedly secures the base 182 of the weight 184 to the flat surface 180 on the inter- V mediate shaft portion 138.
  • the intermediate extension 140 also includes a flat connector surface 190 against which is located the base 192 of a second counterweight 194.
  • the counterweight 194 includes segments 196 thereon located radially outwardly of the outer surface of the bearing extension 150.
  • the base of the weight is connected by means of a screw 198 to the surface 190.
  • the segments 196, 186 of the counterweights are located outboard of the cross bores in the compressor and in surrounding relationship to the main bearing to balance the inertial effect of the eccentric and the drive portions on the main bearings during compressor operation while retaining a compact compressor configuration from front to rear thereof.
  • Another feature of the present invention is the manner in which the pistons are coupled together in driving relationship with respect to the slider block 120.
  • a plurality of separate elongated needle bearings 200 are inserted between the outer periphery of the shaft eccentric 136 and a bore 202 through the slider block 120.
  • a needle retainer plate or element 204 has an opening 206 therethrough through which one end of the eccentric 136 fits to locate the element 204 to prevent the needles 200 from moving axially outwardly of the slider block in the direction of the main bearing 128.
  • a needle retainer plate or element 208 has a central opening 210 therein fit over the opposite end of the shaft eccentric 136 to cover the slider block and the ends of the needle 200 to prevent them from moving axially outwardly of the slider blocks in the direction of the main bearing 144.
  • the retainer plates 204, 208 serve to separate yoke components 212, 214 of the mechanism 44 from one another.
  • the yoke 212 is best illustrated in F16. 4 as including an upper end 216 thereon located against a flat side surface 218 of one of the piston stems 114 where it is fixedly secured by a pair of screw elements 220, 224.
  • the yoke 212 includes an elongated slot 225 between the end 216 and an end portion 226 that is fixedly connected to a flat surface 227 on another of the piston extensions 114 by a pair of screw elements 228, 230.
  • the yoke 212 thereby serves to interconnect the separate piston elements 110 in the aligned cross bores 14, 16 to be operated as a unit therein upon oscillation movement of the slider block 120 on the eccentric 136.
  • the yoke 214 as best seen in FIG. 3, includes a pair of spaced apart end portions 232, 234 joined by screw elements 236, 238 and 240, 242 to respective flat surfaces on adjacent piston stems 114.
  • the yoke has an elongated central opening 244 formed betweeen the ends 232, 234 to permit opposite reciprocation of the joined pistons within the aligned cross bores 18, 20 by the sliding movement of the flat surfaces 118 on the slider block 120 as it is driven by the eccentric 136 to and fro across the flat ends 116 of the pistons.
  • the yokes are maintained separate from one another by the needle retainer plates 204, 208 throughout the complete revolution of the slider block 120 with respect to the piston.
  • each of the pistons 110 includes a tenacle 245 thereon which is upset against a retainer washer 246 that engages the inner periphery of the disc248 forming a suction valve which opens and closes with respect to a plurality of circumferentially located suction openings 250 in the head of the piston 110.
  • the disc 248 will flex with respect to its centrally retained portion away from the head of the piston 110 as the piston 110 moves from one of the cylinder bores. During this motion, low pressure gas within the cavity is drawn into the cylinder bore.
  • one of the pistons will be moved towards the one of the retainer discs so as to compress gas into the bore to discharge it across the rectangularly configured discharge valve reed 96 into the annular high pressure cavity 62.
  • the slider block will progressively reciprocate each of the pistons within their cylinder bores to produce a progressive withdrawal of low pressure gas from the suction cavity and a progressive discharge of high pressure gas into the discharge cavity 62.
  • the suction cavity occupies a substantial part of the internal volume of the two piece compressor formed by the housing 12 and the outer shell 34 and hence constitutes a large volume gas space for muffling noise on the suction side of the compressor.
  • the continuously formed O-ring seals 77 and 84 seal the annular cavity 62 including the muffler cavities 66 therein to isolate the high pressure side of the compressor from the low pressure side thereof.
  • a superheat switch 251 is supported in a bore 252 formed in another boss 254 on the rear wall 22 at a point adjacent the suction bore therein.
  • the superheat switch is a device which senses the condition of the refrigerant on the suction side of the compressor in order to terminate compressor operation under certain operating conditions.
  • a lubricant bleed passageway 258 is formed between the bore of the superheat switch and the suction cavity to serve as a path for return flow of lubricant from another portion of the automotive refrigeration system in which the compressor is included as an operative component.
  • the arrangement thus has a highly compact cubical con-figuration especially suited for location in the limited confines of an automobile engine compartment. Further, its weight is reduced in the order of 50 percent Torque 10-12 foot-pounds (lOOO-3000 rpm) Capacity 12 BTU/HR-IOOO at 1000 rpm 24 BTU/HR-IOOO at 2000 rpm 31 BTU/HR-lOOO at 3000 rpm Isentropic Efficiency 65% at 1000 rpm 60% at 2000 rpm 55% at 3000 rpm Volumetric Efficiency at 1000 rpm 66% at 2000 rpm 60% at 3000 rpm While the embodiment of the present invention, as herein disclosed, constitutes a preferred form, it is to be understood that other forms might be adopted.
  • a compressor comprising, an integral cylinder housing with four cross bores formed therein to intersect in a common plane, said cylinder housing including a front wall and an exterior rear wall, each of said walls generally radially extending beyond said bores and adapted to define an annular outer discharge space in communication with said bores, said front wall including a central opening therein, a central suction space within said housing in communication with said front wall opening and each of said cross bores, a suction port for directing return gas into the central suction space, means including a discharge port for directing discharge gas from said cross bores, said housing having spaces circumferentially between adjacent cylinder bores of the housing forming muffler cavities which are in communication with said discharge spaces but are sealed off by wall portions of the cylinder housing from said central suction space, a piston located in each of said cross bores, a bearing hub in said rear wall located centrally thereof, means forming a bearing housing located coaxially of said bearing hub and said front wall opening, a shaft having first and second journal portions thereon rotatably
  • a compressor comprising a cylinder housing having four cross bores therein located in the same plane, a central suction space within said cylinder housing communicating with each of said cross bores, an inte' gral rear wall closing said central suction space on one end of said cylinder housing, an integral front wall on the other end thereof, said front and rear walls extending generally radially and including respective peripheral portions formed continuously therearound, means forming a suction inlet in said rear wall, a plate located within each of said bores having the peripheral edge thereof in engagement with each of said front and rear walls of said cylinder housing, an annular sheet metal closure member located in surrounding relationship to said cylinder housing having an inner surface thereon maintained in juxtaposed relationship with the surfaces of the continuously formed peripheral portions of said rear wall and said front wall, means for retaining said sheet metal closure member on said cylinder housing, means for sealing between said cylinder housing and said sheet metal closure member completely circumferentially therearound to define an annular high pressure discharge space formed radially outwardly of each of said cross bores and each of said cross bores communicating
  • a compressor having an integral cylinder housing with four cross bores therein intersecting in a common plane, said cylinder housing having a centrally located suction cavity therein, an exterior rear cylinder wall closing one end of said central suction cavity, a front cylinder wall having a central opening therein, said rear cylinder wall having a centrally located inwardly directed axial hub thereon, a bore within said hub defining a first bearing, means defining a bearing housing located outwardly of said cylinder housing front wall including a bore therein defining a second bearing in alignment with said first bearing, an integral drive shaft having first and second journal portions thereon supported respectively in said first bore and said second bore, a shaft portion between said first and second journal portions located eccentrically with respect thereto and in said central suction cavity, an inclined shaft portion on each end of said eccentric shaft portion integrally connecting it with said first and second shaft journal portions for reducing the width between said journal portions and to locate main shaft bearings close to crank arm loads to reduce shaft moments, a slider block having a central opening therein located coaxially
  • a compressor including an integral cylinder housing having four cross bores located therein and intersecting in a common plane, a central suction cavity within said cylinder housing in communication with each of said cross bores, said cylinder housing having a rear wall closing one end of said suction cavity, said cylinder housing having a front wall at the other end of said suction cavity with an opening therein, a suction inlet in said rear wall for directing return gas into said suction cavity centrally of said cylinder housing, a first bearing on said rear housing, means defining a second bearing located in alignment with said first bearing at a point centrally of the opening in said front wall, a shaft having first and second journal portions thereon supported by said first and second bearings for rotation with respect thereto, a piston in each of said cylinder bores, drive means within said central suction cavity for exposure to said return gas and connecting said shaft to each of said pistons for causing opposite reciprocation of each of said pistons within said cross bores upon rotation of said shaft, a sheet metal closure having an annular peripheral segment thereon overlying
  • a compressor for an automotive refrigeration system adapted to be operated at speeds up to 3000 revolutions per minute comprising a rigid cast single piece cylinder housing having generally circular front and rear walls defining therebetween four cross bores intersecting in a common plane, a central low pressure suction space within said cylinder housing communcating with each of said cross bores, said rear wall closing said central suction space on one end of said cylinder housing, means for closing said central suction space at the other end of said cylinder housing, means forming a suction port in said rear wall in communication with said suction space and adapted for connection with said refrigeration system, a retainer plate located within each of said bores and having the peripheral edge thereof in engagement with each of said front and rear walls of said cylinder housing, an annular sheet metal closure member located in surrounding relationship to said cylinder housing having an inner surface thereon in engagement with the outer periphery of said rear wall and said front wall, means for retaining said sheet metal closure member on said cylinder housing, means for sealing between said cylinder housing and said sheet metal closure member at their said engagement completely circum
  • a compressor comprising a rigid cast single piece cylinder housing with four cross bores formed in intersecting relation in a common plane therein between generally radially extending front and rear walls of the housing that include respective peripheral portions formed continuously therearound, said front wall including a central opening therein, a central suction space within said housing in communication with said front wall opening and each of said cross bores, a suction port in said rear wall for directing return gas into the central suction space, means including a discharge port in said rear wall for directing discharge gas from said cross bores, a piston located in each of said cross bores, a bearing hub in said rear wall locatedcentrall thereof and in communication with said central suction space by lubricant bleed passageway means, means forming a bearing housing located coaxially of said bearing hub and said front wall opening and in communication with said central suction space by lubricant bleed passageway means, a shaft having generally solid first and second journal portions thereon rotatably sup ported respectively in said bearing hub and said bearing housing, a shaft eccentric portion located in
  • a radial compressor comprising a rigid cast singlepiece cylinder housing having four cross bores which are disposed in radial cylinder portions of the housing and intersect in a common plane between generally radially extending front and exterior rear walls of the housing that include respective peripheral portions formed continuously theraround, said housing having discharge regions at the radially outer ends of the respective cross bores and a central suction space in communication with the radially inner ends of said respective cross bores, said central suction space being de fined on one side by the rear wall of said housing and on the other side by a central opening in the front wall of said housing, said housing having spaces circumferentially between adjacent cylinder portions of the housing forming muffler cavities which are in communication with said discharge regions but are sealed off by wall portions of the cylinder housing from said central suction space, an exterior annular sheet metal closure member retained on the cylinder housing in a position surrounding the cross bores and having an inner surface maintained in sealing relationship with surfaces of the continuously formed peripheral portions of the front and rear walls of the cylinder housing to thereby define an annular
  • shell 72' H1 should read shell wall 72 calm 4 line 58, "extien-sion” should read extension Column 6 1 lines 66 67,

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Abstract

A compact high capacity rotary refrigerant compressor suitable for use in automotive refrigeration systems including a cylinder housing having cross bores formed therein. Front and rear cylinder walls support a circumferentially located sheet metal shell sealed to form a continuously circumferential high pressure discharge space with enlarged discharge muffler cavities. A short shaft and bearing assembly is formed between the front and rear walls to reduce compressor length. The sheet metal shell and cylinder housing form a sealed suction cavity located centrally of the sealed discharge space.

Description

United States Patent 1191 Heidorn 1 Jan. 8, 1974 [54] RADIAL COMPRESSOR WITH TWO-PIECE 1,383,657 7/1921 Noguera 417/273 CYLINDER HOUSING AND SHELL 3,685,923 8/1972 Hutchins .1 417/523 [75] Inventor: John H. Heidorn, Dayton, Ohio FOREIGN PATENTS OR APPLICATIONS 367,790 2/1939 Italy 417/273 [73] Asslgme' Minors Corpmatwn 1,022,273 12 1952 France 417/534 Detro1t, M1ch.
1 Filed! y 1972 Primary Examiner-William L. F'reeh [211 App]. 254,511 Attorney-Sidney Carter et al.
52 U.S. c1. 417/273 [571 ABSTRACT [51] Int. Cl. F04b 1/04 A compact high capacity rotary refrigerant compresl l Field of Search sor suitable for use in automotive refrigeration systems 4 /5 2/138 including a cylinder housing having cross bores formed therein. Front and rear cylinder walls support [56] References Cited a circumferentially located sheet metal shell sealed to UNITED STATES PATENTS form a continuously circumferential high pressure dis- 3 695 786 10 1972 Gannaway 417/273 charge space with enlarged dischmge cavities- 3:008:628 11/1961 Gerteis 417 419 A Short Shaft and bearing assembly is formed between 2,752,088 6/1956 Bogerd et a1. 417/567 the front and rear walls to reduce compressor length. 2,893,626 7/1959 Weibel 417/419 The sheet metal shell and cylinder housing form a 3,174,436 3/1965 Wanner.... 1. 417/273 sealed suction cavity located centrally of the sealed 2,935,248 5/l960 6811815 417/571 discharge pace; 3,456,874 7/1969 Graper 417/534 1,631,425 6/1927 Marcus 417/273 11 Claims, 7 Drawing Figures //fl /f1' Z57 W 15" W Z {I 32%; 3 /42 W 2 f4 470 w Z T Q //f 7/ 7444/24 6? y t A? -7 //2 A? 7 if? 2% 250 a? z 7;): 3 Z 21% x0 47 4 #1 I? 32 y if? 2 H HZ VPAIENTEDJAH M 3.784.331
SHEEI 2 BF 3 1 RADIAL COMPRESSOR WITH TWO-PIECE CYLINDER HOUSING AND SHELL This invention relates to automotive refrigeration compressors and more particularly to a compact refrigerant compressor of the type including a rigid cylinder housing having cross bores formed therein with reciprocating pistons operated by a drive shaft extending externally of the compressor housing.
Automotive refrigeration systems typically have the component parts thereof located within a limited space inside the engine compartment of a vehicle. It is desirable that the refrigeration compressor have a substantial capacity without occupying too much of the engine compartment space of a vehicle. One method to accomplish this purpose is to reduce the front to rear dimensions of refrigerant compressors for the use in vehicles.
One well known type of pump which has a reduced front to rear dimensional configuration is the type of pump or compressor which includes a plurality of radial cylinder bores each including a piston reciprocated with respect to the bores for compressing and discharging gas.
In such arrangements, each of the cylinders are located in a common plane to reduce the front to rear di mension of the compressor.
An object of the present invention is to improve a compressor having radially located across bores therein, each with a reciprocating piston for compressing gas by the provision of an improved short shaft configuration within the compressor having main bearings located close to crank arm loads to reduce shaft movements.
Still another object of the present invention is to provide an improved high capacity compressor with a large discharge volume therein formed by a sheet metal shell having surface portions thereon sealingly engaged with continuous annular seals in a rigid cylinder bore housing including a rear wall and a front wall forming the front and rear of the large discharge volume in the compressor and wherein the cylinder housing includes a central suction cavity completely circumferentially surrounded by a large volume discharge space to muffle compressor noise.
Still another object of the present invention is to provide an improved compact high capacity compressor for use in automotive air conditioning systems includ ing a rigid cylinder housing having cross bores therein supporting a metal shell which includes a conical surface on one end thereof in which is located a rigid bearing housing, a conical surface locating the first bearing in alignment with a second bearing on a rigid wall of the cylinder housing to align shaft end portions for rotation with respect to said cylinder housing.
Further objects and advantages of the present invention will be apparent from the following description, reference being had to the accompanying drawings wherein a preferred embodiment of the present invention is clearly shown.
In the drawings:
FIG. 1 is a view in vertical section through a compressor including the present invention;
FIG. 2 is a fragmentary view in horizontal section taken along the line 2--2 of FIG. I looking in the direction of the arrows;
FIG. 3 is a vertical sectional view taken along the line 3-3 of FlG. 1 looking in the direction of the arrows;
FIG. 4 is a fragmentary sectional view taken along the line 4-4 of FIG. I. looking in the direction of the arrows;
FIG. 5 is an end elevational view of the cylinder housing of the compressor in FIG. I;
FIG. 6 is a fragmentary sectional view taken along the line 6-6 of FIG. 5; and
FIG. 7 is a fragmentary sectional view taken along the line 7--7 of FIG. 5.
Referring now to the drawings, :in FIG. 1 a compressor 10 is illustrated. It includes a rigid cast cylinder housing 12 having radially located cross bores 14, 16 on one axis of the cylinder housing. A second pair of cross bores 18, 20 are formed on a second axis of the housing 12 at a right angular or cross relationship to the bores l4, 16 as is best seen in FIG. 3.
The cylinder housing 12 has a circular configuration as seen in FIG. 5 which is intersected by the cross bores. The circular configuration and the cross bore arrangement produces an extremely compact planar configuration of the compressor as viewed in end elevation. The housing includes a rear wall 22. It has an outwardly directed central boss 24 thereon surrounded by a concentric stepped wall segment 25 integrally joined with a radially outwardly located, bore forming, thin sectioned wall segment 26 having an enlarged peripheral flange 28 thereon. An inclined surface 30 on the outer face of the flange 28 is inclined inwardly of the rear wall 22 continuously therearound. It defines a clamp surface located in interlocking relationship with the bent end 32 of an outer sheet metal shell 34.
One feature of the present invention is that the cylinder housing 12 and the outer sheet metal shell 34 form a two-piece construction which is easily assembled to form an unusually compact suction cavity and discharge chamber and muffler cavity configuration located between the rear wall 22 of the housing and a front wall 36 thereon which has an enlarged peripheral flange 38 thereon with a front bearing face 40.
The peripheral flange 38 is formed continuously around the front edge of the housing 12. Likewise, the front wall 36 is circular and has a radially inwardly directed edge thereon forming a central opening 42 in the wall through which a short shaft drive mechanism 44 fits.
The drive mechanism 44 more particularly is located interiorly of the cylinder housing within a low pressure suction space or cavity 46 therein. The suction cavity 46 communicates with a suction port 48 formed through an inclined boss 50 extending outwardly ofthe rear wall 22 at an angle to communicate with a side cutout portion of the suction cavity 46 in the housing 12 as is best seen in FIG. 7. A suction screen 52 having an elongated conical configuration has a head portion 54 thereon seated in the port 48 for removing particles from return gas passing into the compressor during its operation.
Additionally, the rear wall 22 includes a discharge port 56 which isformed in an outwardly angularly inclined boss 58 on the outer surface of the end wall 22. Port 56 is in intersecting relationship with one end of a passageway 60 which has the opposite end thereof in communication with a portion of an annular high pressure cavity 62 formed between the outer shell 34 and the outer periphery of the cylinder housing 12. The inclined configuration of boss 50 and boss 58 reduces the length of space required for mounting the compressor and connecting it to hoses in the refrigerant system.
The housing 12 in addition to the rear wall 22 and the front wall 36 includes circumferentially spaced cut out walls 64 therein which form a muffler cavity 66 between each of the cross bores in the housing 12. Each of the cavities 66 serve to muffle high pressure gas discharged from the cross bores during compressor operation. Each cut out wall 64 includes a base segment 68 which is in heat exchange relationship with cool return gas from the suction port 48. Additionally, the cavities 66 are located closely circumferentially adjacent an upper narrow opening 70 between the housing 12 and shell 34 communicating each of the cross bores with the cavity 62.
The suction cavity 46 and the annular high pressure cavity 62 are sealed apart from one another between the two pieces made up by the cylinder housing 12 and the outer shell 34. More particularly, as illustrated in FIGS. 1 and 2, the shell 34 includes a circular peripheral wall 72 having an inner surface stepped at 74 and at 76. The stepped portion 74 is a continuous circumferential surface which is in sealing engagement with an O-ring seal 77 circumferentially located continuously within a circular groove 78 in the outer periphery of the flange 28 completely therearound.
The stepped portion 76 locates the outer shell 34 against the radially outer peripheral edge of the flange 38. The shell includes a radially inwardly bent segment 80 thereon formed continuously around the front outer periphery of the shell. It has an inner surface 82 thereon which is located in sealing engagement with an O-ring seal 84 formed continuously circumferentially around the front bearing face 40 on the front wall 36. The bent edge 32 on the shell is spun over against the surface 30 so as to cause the shell surface 82 to be drawn into sealing engagement with the O-ring seal 84 and to force the stepped portion 74 into sealing engagement with the O-ring seal 77. The inclination on the support surface 30 and the spun over edge 32 cooperate to produce a clamped interconnection between the two pieces constituted by the housing 12 and the shell 34 to resist pressure forces in the high pressure cavity 62 tending to cause these parts to separate radially with respect to one another.
In the arrangement, the spun over edge 32 and the inner surface 82 are drawn together so as to produce a peripheral force on each of the cross bores at the radially outermost ends thereof.
In accordance with certain principles of the present invention, a rigid member or shell reinforcing retainer or plate 86 is located in seated relationship in a counterbore 87 in each of the bores. The reinforcing retainer disc 86 has the peripheral edge thereof located in juxtaposed relationship withthe inside surface of each of the bores at the bearing point between the inner surface 82 on the outer shell and the front bearing face 40 thereon. Likewise, the retainer reinforces the stepped wall segment 26 of the housing which forms the opposite wall of each of the bores. It also serves to reinforce the cut out walls 64.
The retainer disc 86, as best seen in FIGS. 2 and 3, includes a pair of spaced holes 88, 90 therein which communicates each of the cross bores with a valve cage opening 92 located between the disc and the outer shell 72. The arrangement eliminates the need for drilling several small holes to produce adequate discharge flow area.
The disc serves as a support for an improved low cost discharge valve assembly 93 which includes parts made of sheet metal stock formed to produce selective opening and closing of the discharge valve openings 88, 90 in the disc during compressor operation.
More particularly, the valve assembly 93 includes an elongated rectangularly shaped reed element 94 having a free end portion 96 thereon movable with respect to a guide slot 97 formed on one side ofa dome valve retainer 98.
In the illustrated arrangement, the dome valve retainer 98 includes a plurality of circumferentially spaced cut out portions 100 in the edge thereof between a plurality of radially outwardly directed fingers 102 which are press fit within the counterbore 87 to hold the disc 86 in place therein. Each of the cut outs 100 serve to communicate the valve cage opening 92 with the peripheral opening 70 between each of the bores and the outer shell 34.
The dome has the top portion 104 thereon in engagement with the inner surface of the peripheral wall 72 to maintain a radially inwardly directed bias on the dome so as to firmly spring bias the fingers 102 into the counterbore and to allow some flexing for changes in heat and pressure.
Additionally, the valve assembly 93 includes a rectangularly configured back-up plate 106 which has a distal end 108 thereon located within the dome slot 97 to overlie the free end 96 of the reed element 94. The
- distal end 108 is supported by the dome in this position and will serve to limit outward movement of the reed away from the openings through the disc during a compression stroke.
The dome 98 further includes a downwardly struck tab portion 109 thereon which is directed through fixed ends of the back-up plate 106 and the valve 94 and into interlocked relationship with a slot 111 in one side of the disc 86 thereby to firmly secure the fixed end of both the retainer plate and the valve with respect thereto.
Each of the cross bores supports a piston with an elongated skirt portion 112 slidably supported on the inner surface of the bore for reciprocation with respect thereto. The skirt 112 surrounds an elongated piston stem 114 which includes a flat surface 116 thereon supported by a sliding reciprocating surface 118 ofa slider block 120 on the short shaft drive mechanism 44.
In accordance with certain principles of the present invention, the mechanism 44 is configured to reduce bending moments on a compressor drive shaft by being configured to locate main shaft bearings in close axial relationship with the primary loads on the shaft.
Accordingly, in the illustrated arrangement, the mechanism 44 includes a drive shaft 122 with an outboard exten-sion 124 thereon adapted to be connected to a rotary drive source.
In the illustrated arrangement, the shaft 122 includes an inboard shaft journal 126 supportingly received by a main needle bearing 128 located in a bearing bore 130 formed in a tubular extension 132 in line with the central boss 24 on the rear wall 22 and directed axially inwardly thereof.
The journal 126 is supported substantially throughout its length by the main bearing 128 and a thrust washer 134 which fits over the shaft journal 126 to engage the end of the tubular extension 132.
A shaft eccentric portion 136 is joined to the shaft journal 126 by an intermediate shaft portion 138 of a short length and having an inclination with respect to the axis of the shaft through the extension 124 and the journal 126. Likewise, the shaft includes a second inclined portion 140 joining the eccentric 136 to a sec ond shaft journal portion 142 which is supported by a second main bearing 144.
In accordance with certain principles of the present invention, the main bearing 144 for the shaft journal 142 is supported on the outer shell 34. The outer shell constitutes a sheet metal bearing support to align the bearing supported shaft portions during compressor operation.
More particularly, the outboard bearing support for the shaft portion 132 is constituted by a conically configured axial extension 145 formed integrally with the bent segment 80 of the shell 34. It includes a radially inwardly directed support surface 146 arranged generally perpendicularly with respect to the axis of the drive shaft 122. The support surface 146 has an opening 148 located centrally thereof directed therethrough in which is located an inward tubular portion 150 of a rigid bearing and seal housing 152.
The housing 152 is connected to the surface 146 by means of a weld 154. The tubular extension 150 includes a bearing bore 156 therein in which is located the second main bearing 144 having needles 158 to rotatably support the shaft journal portion 142.
The housing 152 is closely aligned to locate the bore 156 coaxially of the bore 130 whereby the shaftjournal portions 126, 142 are supported on the main bearings in accurate axial alignment with one another. By virtue of the inclined shaft portions 138, 140 and the configuration of the tubular extensions 132, 150 the mechanism 44 has a short shaft with the main bearings closely adjacent the shaft eccentric 136 thereby to reduce the distance between the main forces on the shaft eccentric and the main bearing points to reduce shaft moments.
The rigid housing 152 is supported by the conical extension 145 on the outer shell 34 to produce a controlled amount of flexure to assure alignment of the bores 130, 156.
Outboard of the shell 34 the housing 152 includes a large diameter bore 160 in which is located a rotary shaft seal assembly 162. The shaft seal is of a conventional type including a seal ring 164 fixed by means of a retainer ring 166 within a counterbore in the housing 152. The ring 164 is sealed by means of an O-ring seal 168 at the outer periphery thereof. it includes an axially inwardly locatedface 170 in sliding sealing engagement with the face 172 of a rotary seal 174 carried by a conical spring 176 and bracket 178 secured on the shaft 122 for rotation therewith.
In addition to aligning the main bearings of the compressor with one another, the seal housing 152 along with the seal assembly 162 therein will seal the shaft against leakage of gas from the low pressure suction cavity 46.
In addition to the dynamic stability provided by the location of the shaft journals in close proximity to the loaded portion of the shaft the improved short shaft mechanism 44 includes an arrangement for locating balanced weights within the short axial limits between the inner and outer walls of the cylindrical housing 12.
More particularly, the inclined intermediate shaft portion 138 includes a flat end surface 180 against which the base 182 ofa counterweight 184 is located.
The counterweight 184 has radially outwardly directed segments 186 thereon located around the outer periphery of the tubular extension 132 for rotation therearound. A screw 188 fixedly secures the base 182 of the weight 184 to the flat surface 180 on the inter- V mediate shaft portion 138.
ln order to provide a balanced Weight couple on the shaft 124, the intermediate extension 140 also includes a flat connector surface 190 against which is located the base 192 of a second counterweight 194.
The counterweight 194 includes segments 196 thereon located radially outwardly of the outer surface of the bearing extension 150. The base of the weight is connected by means of a screw 198 to the surface 190.
By virtue of this arrangement, the segments 196, 186 of the counterweights are located outboard of the cross bores in the compressor and in surrounding relationship to the main bearing to balance the inertial effect of the eccentric and the drive portions on the main bearings during compressor operation while retaining a compact compressor configuration from front to rear thereof.
Another feature of the present invention is the manner in which the pistons are coupled together in driving relationship with respect to the slider block 120.
More particularly, in the illustrated arrangement, a plurality of separate elongated needle bearings 200 are inserted between the outer periphery of the shaft eccentric 136 and a bore 202 through the slider block 120. A needle retainer plate or element 204 has an opening 206 therethrough through which one end of the eccentric 136 fits to locate the element 204 to prevent the needles 200 from moving axially outwardly of the slider block in the direction of the main bearing 128. Likewise, on the opposite side of the slider block, a needle retainer plate or element 208 has a central opening 210 therein fit over the opposite end of the shaft eccentric 136 to cover the slider block and the ends of the needle 200 to prevent them from moving axially outwardly of the slider blocks in the direction of the main bearing 144.
In addition to retaining the needles between the eccentric and the slider block, the retainer plates 204, 208 serve to separate yoke components 212, 214 of the mechanism 44 from one another. The yoke 212 is best illustrated in F16. 4 as including an upper end 216 thereon located against a flat side surface 218 of one of the piston stems 114 where it is fixedly secured by a pair of screw elements 220, 224. The yoke 212 includes an elongated slot 225 between the end 216 and an end portion 226 that is fixedly connected to a flat surface 227 on another of the piston extensions 114 by a pair of screw elements 228, 230.
The yoke 212 thereby serves to interconnect the separate piston elements 110 in the aligned cross bores 14, 16 to be operated as a unit therein upon oscillation movement of the slider block 120 on the eccentric 136.
Likewise, the yoke 214, as best seen in FIG. 3, includes a pair of spaced apart end portions 232, 234 joined by screw elements 236, 238 and 240, 242 to respective flat surfaces on adjacent piston stems 114. The yoke has an elongated central opening 244 formed betweeen the ends 232, 234 to permit opposite reciprocation of the joined pistons within the aligned cross bores 18, 20 by the sliding movement of the flat surfaces 118 on the slider block 120 as it is driven by the eccentric 136 to and fro across the flat ends 116 of the pistons.
The yokes are maintained separate from one another by the needle retainer plates 204, 208 throughout the complete revolution of the slider block 120 with respect to the piston.
In the illustrated arrangement each of the pistons 110 includes a tenacle 245 thereon which is upset against a retainer washer 246 that engages the inner periphery of the disc248 forming a suction valve which opens and closes with respect to a plurality of circumferentially located suction openings 250 in the head of the piston 110. The disc 248 will flex with respect to its centrally retained portion away from the head of the piston 110 as the piston 110 moves from one of the cylinder bores. During this motion, low pressure gas within the cavity is drawn into the cylinder bore. Concurrently, one of the pistons will be moved towards the one of the retainer discs so as to compress gas into the bore to discharge it across the rectangularly configured discharge valve reed 96 into the annular high pressure cavity 62. The slider block will progressively reciprocate each of the pistons within their cylinder bores to produce a progressive withdrawal of low pressure gas from the suction cavity and a progressive discharge of high pressure gas into the discharge cavity 62.
The suction cavity occupies a substantial part of the internal volume of the two piece compressor formed by the housing 12 and the outer shell 34 and hence constitutes a large volume gas space for muffling noise on the suction side of the compressor. Likewise, on the discharge side of the compressor, there is a substantial gas volume located also between the front and rear walls of the single piece housing 12 to muffle noise on the discharge of the compressor.
The continuously formed O- ring seals 77 and 84 seal the annular cavity 62 including the muffler cavities 66 therein to isolate the high pressure side of the compressor from the low pressure side thereof.
in the illustrated arrangement, a superheat switch 251 is supported in a bore 252 formed in another boss 254 on the rear wall 22 at a point adjacent the suction bore therein. The superheat switch is a device which senses the condition of the refrigerant on the suction side of the compressor in order to terminate compressor operation under certain operating conditions.
it is sealed with respect to the housing by means of an O-ring seal 256. A lubricant bleed passageway 258 is formed between the bore of the superheat switch and the suction cavity to serve as a path for return flow of lubricant from another portion of the automotive refrigeration system in which the compressor is included as an operative component.
One working embodiment of the invention has the following mechanical and physical characteristics:
Displacement 6 to cubic inches Length 6.98 inches Width 6.90 inches Height 6.90 inches Weight ll.5 pounds The arrangement thus has a highly compact cubical con-figuration especially suited for location in the limited confines of an automobile engine compartment. Further, its weight is reduced in the order of 50 percent Torque 10-12 foot-pounds (lOOO-3000 rpm) Capacity 12 BTU/HR-IOOO at 1000 rpm 24 BTU/HR-IOOO at 2000 rpm 31 BTU/HR-lOOO at 3000 rpm Isentropic Efficiency 65% at 1000 rpm 60% at 2000 rpm 55% at 3000 rpm Volumetric Efficiency at 1000 rpm 66% at 2000 rpm 60% at 3000 rpm While the embodiment of the present invention, as herein disclosed, constitutes a preferred form, it is to be understood that other forms might be adopted.
I claim:
1. A compressor comprising, an integral cylinder housing with four cross bores formed therein to intersect in a common plane, said cylinder housing including a front wall and an exterior rear wall, each of said walls generally radially extending beyond said bores and adapted to define an annular outer discharge space in communication with said bores, said front wall including a central opening therein, a central suction space within said housing in communication with said front wall opening and each of said cross bores, a suction port for directing return gas into the central suction space, means including a discharge port for directing discharge gas from said cross bores, said housing having spaces circumferentially between adjacent cylinder bores of the housing forming muffler cavities which are in communication with said discharge spaces but are sealed off by wall portions of the cylinder housing from said central suction space, a piston located in each of said cross bores, a bearing hub in said rear wall located centrally thereof, means forming a bearing housing located coaxially of said bearing hub and said front wall opening, a shaft having first and second journal portions thereon rotatably supported respectively in said bearing hub and said bearing housing, a shaft eccentric portion located in the same plane as each of said cross bores and in said central suction space, inclined intermediate shaft portions integrally connecting each of said shaft journal portions with said shaft eccentric portion for locating main shaft bearing points close to crank arm loads to reduce shaft moments, each of said inclined shaft portions having a connection surface thereon offset from the longitudinal axis of said first and second shaft journal portions, a first counterweight having a leg portion thereon located around one of said shaft journal portions, means for fixedly securing said first counterweight leg portion to the connection surface on one of said inclined shaft portions, said first counterweight having a radially outwardly located offset portion thereon located axially outwardly of said inclined shaft portion at a point radially outwardly of said bearing hub, a second counterweight having a leg portion thereon in engagement with the connection sfrface on the other inclined shaft portion axially outwardly of the plane of each of said cross bores, means for securing said second counterweight leg portion to said last-mentioned connection surface, said second counterweight having a portion thereon located axially outwardly of said cylinder housing and radially outwardly of said bearing housing, drive means in said central suction space between said shaft eccentric portion and said pistons for causing reciprocation of said pistons within said cross bores upon rotation of said shaft, the jointure between said shaft eccentric portion and said drive means being in said central suction space and exposed to said return gas, said first and second counterweights serving to balance the inertia of said offset shaft eccentric portion and said drive means during operation of said compressor.
2. A compressor comprising a cylinder housing having four cross bores therein located in the same plane, a central suction space within said cylinder housing communicating with each of said cross bores, an inte' gral rear wall closing said central suction space on one end of said cylinder housing, an integral front wall on the other end thereof, said front and rear walls extending generally radially and including respective peripheral portions formed continuously therearound, means forming a suction inlet in said rear wall, a plate located within each of said bores having the peripheral edge thereof in engagement with each of said front and rear walls of said cylinder housing, an annular sheet metal closure member located in surrounding relationship to said cylinder housing having an inner surface thereon maintained in juxtaposed relationship with the surfaces of the continuously formed peripheral portions of said rear wall and said front wall, means for retaining said sheet metal closure member on said cylinder housing, means for sealing between said cylinder housing and said sheet metal closure member completely circumferentially therearound to define an annular high pressure discharge space formed radially outwardly of each of said cross bores and each of said cross bores communicating with said discharge space, said cylinder housing having circumferentially located radially inwardly formed wall cutouts therein in communication with said discharge space to define circumferentially spaced discharge muffler cavities between said front and rear walls of said cylinder housing, said plate engaging the front and rear walls of said housing at said wall cutouts, means forming a discharge opening in said cylinder housing rear wall in communication with said high pressure discharge space for communicating each of said circumferentially spaced discharge muffler cavities with the outside of said compressor, a piston in each of said cross bores, means including an integral eccentrically offset rotary drive shaft in said central suction space for reciprocating each of said pistons within said cross bores, suction valve means on each of said pistons for drawing gas from said suction inlet through said suction space into each of said cross bores, discharge valve means on said plate for directing compressed gas from each of said cross bores into said annular high pressure discharge space.
3. A compressor having an integral cylinder housing with four cross bores therein intersecting in a common plane, said cylinder housing having a centrally located suction cavity therein, an exterior rear cylinder wall closing one end of said central suction cavity, a front cylinder wall having a central opening therein, said rear cylinder wall having a centrally located inwardly directed axial hub thereon, a bore within said hub defining a first bearing, means defining a bearing housing located outwardly of said cylinder housing front wall including a bore therein defining a second bearing in alignment with said first bearing, an integral drive shaft having first and second journal portions thereon supported respectively in said first bore and said second bore, a shaft portion between said first and second journal portions located eccentrically with respect thereto and in said central suction cavity, an inclined shaft portion on each end of said eccentric shaft portion integrally connecting it with said first and second shaft journal portions for reducing the width between said journal portions and to locate main shaft bearings close to crank arm loads to reduce shaft moments, a slider block having a central opening therein located coaxially of said eccentric shaft portion in said central suction cavity, a plurality of separately insertable elongated round needles supported between said slider block opening and said eccentric shaft portion in said central suction cavity for rotatably supporting said slider block on said eccentric shaft portion, said needles constituting the sole bearing means between said eccentric shaft portion and said slider block opening, a first needle retainer element supported on said eccentric shaft portion and overlying said slider block opening to prevent axial movement of said needles, a second needle retainer element supported on said eccentric shaft portion to prevent axial movement of said needles in an opposite axial direction,,a piston in each of said cylinder bores, a first yoke including an elongated slot therein in surrounding relationship to one of said inclined shaft portions to permit rotation thereof with respect to said first yoke, said first yoke having opposite ends thereon located on one side of a first pair of said pistons, said first yoke having an inside surface thereon in engagement with said needle retainer element to maintain separation from said slidler block, means for securing said opposite yoke ends to the stem portions on each of said pistons for joining said first pair of pistons for concurrent reciprocation within said bores, a second yoke having an inner surface thereon in engagement with said second needleretainer element, said second needle retainer element to maintain separation of said second yoke from said slider block, said second yoke including an elongated opening therein around said second shaft inclined portion to permit rotation thereof with respect to said second yoke, said second yoke having opposite ends thereon located on one side of a second pair of said pistons, means for securing said opposite ends of said second yoke to stems of said second pair of pistons to join said second pair of pistons for concurrent reciprocation within said bores, means forrotating said shaft to cause said slider block to move axially with respect to saidipistons, means coupling said slider block with said pistons to cause opposite reciprocation thereof into and out of said bores, valve means on said pistons for drawing gas from said central suction cavity into one end of each of said cylinder bores, discharge valve means at the opposite end of said cylinder bores to direct compressed gas from each of said cylinder bores, means including an inlet opening to said central suction cavity for directing return gas thereto, and means including an outlet opening to said cylinder housing for receiving high pressure gas from each of said cylinder bore discharge valve means.
4. A compressor including an integral cylinder housing having four cross bores located therein and intersecting in a common plane, a central suction cavity within said cylinder housing in communication with each of said cross bores, said cylinder housing having a rear wall closing one end of said suction cavity, said cylinder housing having a front wall at the other end of said suction cavity with an opening therein, a suction inlet in said rear wall for directing return gas into said suction cavity centrally of said cylinder housing, a first bearing on said rear housing, means defining a second bearing located in alignment with said first bearing at a point centrally of the opening in said front wall, a shaft having first and second journal portions thereon supported by said first and second bearings for rotation with respect thereto, a piston in each of said cylinder bores, drive means within said central suction cavity for exposure to said return gas and connecting said shaft to each of said pistons for causing opposite reciprocation of each of said pistons within said cross bores upon rotation of said shaft, a sheet metal closure having an annular peripheral segment thereon overlying the outer periphery of said cylinder housing to close each of said cross bores therein, each of said cross bores having a rigid member supported therein for reinforcing the front wall of said cylinder housing, said sheet metal closure having a front surface thereon engaged with said front wall of said cylinder housing at the reinforced portion, a conical surface on said closure member directed outwardly of said cylinder housing including a radially inwardly directed central portion thereon, said means defining a second bearing having a housing portion thereon secured to said radially inwardly directed portion of said closure member, means for maintaining a sealed relationship between said front wall of said cylinder housing and said front surface of said closure member and to secure said-closure member on said cylinder housing completely around the outer periphery of said cylinder housing, said cylinder housing having wall means thereon forming a plurality of cut outs therein at circumferentially located spots therearound between each of said cylinder bores to define a plurality of discharge muffler cavities, said cylinder housing and said closure member defining a space communicating each of said cylinder bores with said circumferentially spaced muffler cavities, said rigid reinforcing member reinforcing said housing at each of said cavities, said sheet metal closure member including an inner surface thereon formed continuously around said cylinder housing, an annular seal in said cylinder housing in engagement with inner surface of said closure member to seal between the rear wall of said cylinder housing and said closure member, said rear wall having a clamp surface thereon formed axially inwardly and continuously therearound, said sheet metal closure member having an edge portion thereon bent over and into engagement with said inclined clamp surface to force the front surface of said closure member against the front wall of said cylinder housing and to clamp the circumferential portion of said closure member in sealing engagement with said annular seal, said bent over edge portion connecting with said inwardly directed continuously formed clamp surface of said rear wall to prevent separation of said closure member from said cylinder housing upon pressurization of the chamber formed therebetween.
5. A compressor for an automotive refrigeration system adapted to be operated at speeds up to 3000 revolutions per minute comprising a rigid cast single piece cylinder housing having generally circular front and rear walls defining therebetween four cross bores intersecting in a common plane, a central low pressure suction space within said cylinder housing communcating with each of said cross bores, said rear wall closing said central suction space on one end of said cylinder housing, means for closing said central suction space at the other end of said cylinder housing, means forming a suction port in said rear wall in communication with said suction space and adapted for connection with said refrigeration system, a retainer plate located within each of said bores and having the peripheral edge thereof in engagement with each of said front and rear walls of said cylinder housing, an annular sheet metal closure member located in surrounding relationship to said cylinder housing having an inner surface thereon in engagement with the outer periphery of said rear wall and said front wall, means for retaining said sheet metal closure member on said cylinder housing, means for sealing between said cylinder housing and said sheet metal closure member at their said engagement completely circumferentially therearound to define an an nular high pressure discharge space formed radially outwardly of each of said cross bores, each of said cross bores communicating with said discharge space through its respective retainer plate, said cylinder housing having circumferentially located radially inwardly formed wall cutouts therein in communication with said discharge space to define circumferentially spaced discharge muffler cavities between said front and rear walls of said cylinder housing and between adjacent cylinder bores, each of said retainer plates engaging said housing at said wall cutouts to separate each of said cross bores from said discharge space at the point of communication therebetween, means forming a discharge port in said rear wall in communication with said discharge space and adapted for connection with said refrigeration system for placing all of said circumferentially spaced discharge muffler cavities in communication with said refrigeration system, piston means slidably supported by the inner surface of each of said cross bores, means including a bearing mounting in communication with said central suction space for reciprocating each of said piston means within its respective cross bore throughout the sliding movement of each of said piston means when said compressor is operated at said speeds up to 3000 revolutions per minute, suction valve means supported on each of said piston means for drawing low pressure gas from said suction port through said suction space into each of said cross bores, discharge valve means supported on each of said retainer plates for directing compressed high pressure gas from each of said cross bores into said annular high pressure discharge space.
6. A compressor comprising a rigid cast single piece cylinder housing with four cross bores formed in intersecting relation in a common plane therein between generally radially extending front and rear walls of the housing that include respective peripheral portions formed continuously therearound, said front wall including a central opening therein, a central suction space within said housing in communication with said front wall opening and each of said cross bores, a suction port in said rear wall for directing return gas into the central suction space, means including a discharge port in said rear wall for directing discharge gas from said cross bores, a piston located in each of said cross bores, a bearing hub in said rear wall locatedcentrall thereof and in communication with said central suction space by lubricant bleed passageway means, means forming a bearing housing located coaxially of said bearing hub and said front wall opening and in communication with said central suction space by lubricant bleed passageway means, a shaft having generally solid first and second journal portions thereon rotatably sup ported respectively in said bearing hub and said bearing housing, a shaft eccentric portion located in the same plane as each of said cross bores and in said central suction space, inclined intermediate shaft portions located in the same plane as each of said cross bores and integrally connecting each of said shaft journal portions with said shaft eccentric portion for locating main shaft bearing points close to crank arm loads to reduce shaft moments, each of said inclined shaft portions having a connection surface thereon offset from the longitudinal axis of said first and second shaft journal portions, a first counterweight having a leg portion thereon in engagement with the connection surface on one of said inclined shaft portions, means for fixedly securing said first counterweight leg portion to said connection surface thereof, said first counterweight having a radially outwardly located offset portion thereon located axially outwardly of said one of said inclined shaft portions at a point radially outwardly of said bearing hub, a second counterweight having a leg portion thereon in engagement with the connection surface on the other inclined shaft portion, means for fixedly securing said second counterweight leg portion to said lastmentioned connection surface, said second counterweight having a radially outwardly located offset portion thereon located axially outwardly of said other inclined shaft portion at a point radially outwardly of said bearing housing, drive means in said central suction space between said shaft eccentric portion and said pistons for causing reciprocation of said pistons within said cross bores upon rotation of said shaft, the jointure between said shaft eccentric portion and said drive means being in said central suction space and exposed to said return gas, said first and second counterweights serving to balance the inertia of said offset shaft eccentric portion and said inclined intermediate shaft portions and said drive means during operation of said compressor. H
7. The compressor of claim 6 wherein said jointure contains a plurality of separately insertable needles engageable on one side thereof with said shaft eccentric portion and engageable on the other side thereof with said drive means, said needles constituting the sole bearing means between said eccentric portion and said drive means.
8. A radial compressor comprising a rigid cast singlepiece cylinder housing having four cross bores which are disposed in radial cylinder portions of the housing and intersect in a common plane between generally radially extending front and exterior rear walls of the housing that include respective peripheral portions formed continuously theraround, said housing having discharge regions at the radially outer ends of the respective cross bores and a central suction space in communication with the radially inner ends of said respective cross bores, said central suction space being de fined on one side by the rear wall of said housing and on the other side by a central opening in the front wall of said housing, said housing having spaces circumferentially between adjacent cylinder portions of the housing forming muffler cavities which are in communication with said discharge regions but are sealed off by wall portions of the cylinder housing from said central suction space, an exterior annular sheet metal closure member retained on the cylinder housing in a position surrounding the cross bores and having an inner surface maintained in sealing relationship with surfaces of the continuously formed peripheral portions of the front and rear walls of the cylinder housing to thereby define an annular high pressure discharge space disposed radially outwardly of the cross bores and in com munication with said discharge regions of the cross bores and with said muffler cavities, a generally annular bearing support member closing said central opening in the front wall and forming, in conjunction with a bearing hub that is formed centrally in the rear wall and in tegral therewith, a bearing mounting for a rotary drive shaft in communication with said central suction space, a plurality of apertured pistons slidably mounted within the respective cross bores, a rotary drive shaft in said bearing mounting adapted to effect reciprocation of said pistons within said respective cross bores, an apertured rigid valve plate located within each of the cross bores radially outwardly of the respective piston, with a peripheral edge of each valve plate in engagement with the front and rear walls of the cylinder housing, an intake aperture extending to the central suction space of the cylinder housing, an intake valve on each of the pistons effective, on reciprocation of the piston, to allow gas to pass from the central suction space into a compressive space within the cross bore between the respective piston and valve plate, a discharge valve on each of the valve plates effective, on reciprocation of the respective piston, to supply compressed gasfrom the respective compressive space to the annular high pressure discharge space, and a discharge aperture extending from the annular high pressure discharge space of the cylinder housing to the outside of the compressor.
9. The radial compressor of claim 8 wherein said intake aperture and said discharge aperture extend through said rear wall.
10. The radial compressor of claim 8 wherein the adaptation of said rotary drive shaft to effect reciprocation of said pistons includes as integral portions of the shaft two inclined shaft portions with a shaft eccentric portion therebetween, a slider block having a bore around said eccentric portion, a plurality of separately insertable needles between and in engagement with the outer periphery of said eccentric portion and thebore of said slider block and needle retainer means to prevent said needles from moving axially outwardly of the bore of said slider block, said needles constituting the sole bearing means between said eccentric portion and the bore of said slider block.
cubical configuration for said compressor.
STATES PATENT OFFICE UNKTED fl- Po-mso' 1 5 CERTIFICATE OF CORRECTION F Patet 1 t No. 3, 784,331 Dated Januagg 8, 1974 Invencor($) John H. Heidom It is certified that error appears in the above-identified patent Wand that said Letters Patent are hereby corrected as shown below:
G nnmnmuczo Cited v "Gerteisf' (3,008,628) should read Gerteis et a1 "weibel" Weibel, Jr.
"Marcus" Marcos et a1 "Hutchins" I Hutohins eta].
Column 1 line 28, "acroes'f should read c ross Column 3 lines 52 -53,, should read reizainer di ac "retainer or plate" or l t lines 66 67,
shell 72' H1 should read shell wall 72 calm 4 line 58, "extien-sion" should read extension Column 6 1 lines 66 67,
"betweeen" should read between h3g3 UNITED STATES m'rmr omen CERTiFICATE 0F CORRECTION nun: No. 3.794.331 Dated nuary 8, 1974 Invoncorg'g) John'H. Ibidptn Page It is certified that error appears in the above-identified potent and thatnaid Lettora Potent are horeby corractod as shown bolow:
F I o o *1 11m 12, "tho dim" ahould road. a dim:
line 21, into the" i line 65, coniguration" configuration 1 Q 1m 8 o I line 66,- "sfrface' ahould road surface line 67, "'c'emtzrenll should read centrally line 59, theraround should read thora'around fine 33, compresoive ahould read compression line 37, "compressive" compression Signed and sealed this 1st day of October 197 4.
(SEAL) Attaat:
MCCOY GIBSON JR. C. MARSHALL DANN Attesting Officer Commissioner of Patents

Claims (11)

1. A compressor comprising, an integral cylinder housing with four cross bores formed therein to intersect in a common plane, said cylinder housing including a front wall and an exterior rear wall, each of said walls generally radially extending beyond said bores and adapted to define an annular outer discharge space in communication with said bores, said front wall including a central opening therein, a central suction space within said housing in communication with said front wall opening and each of said cross bores, a suction port for directing return gas into the central suction space, means including a discharge port for directing discharge gas from said cross bores, said housing having spaces circumferentially between adjacent cylinder bores of the housing forming muffler cavities which are in communication with said discharge spaces but are sealed off by wall portions of the cylinder housing from said central suction space, a piston located in each of said cross bores, a bearing hub in said rear wall located centrally thereof, means forming a bearing housing located coaxially of said bearing hub and said front wall opening, a shaft having first and second journal portions thereon rotatably supported respectively in said bearing hub and said bearing housing, a shaft eccentric portion located in the same plane as each of said cross bores and in said central suction space, inclined intermediate shaft portions integrally connecting each of said shaft journal portions with said shaft eccentric portion for locating main shaft bearing points close to crank arm loads to reduce shaft moments, each of said inclined shaft portions having a connection surface thereon offset from the longitudinal axis of said first and second shaft journal portions, a first counterweight having a leg portion thereon located around one of said shaft journal portions, means for fixedly securing said first counterweight leg portion to the connection surface on one of said inclined shaft portions, said first counterweight having a radially outwardly located offset portion thereon located axially outwardly of said inclined shaft portion at a point radially outwardly of said bearing hub, a second counterweight having a leg portion thereon in engagement with the conNection sfrface on the other inclined shaft portion axially outwardly of the plane of each of said cross bores, means for securing said second counterweight leg portion to said lastmentioned connection surface, said second counterweight having a portion thereon located axially outwardly of said cylinder housing and radially outwardly of said bearing housing, drive means in said central suction space between said shaft eccentric portion and said pistons for causing reciprocation of said pistons within said cross bores upon rotation of said shaft, the jointure between said shaft eccentric portion and said drive means being in said central suction space and exposed to said return gas, said first and second counterweights serving to balance the inertia of said offset shaft eccentric portion and said drive means during operation of said compressor.
2. A compressor comprising a cylinder housing having four cross bores therein located in the same plane, a central suction space within said cylinder housing communicating with each of said cross bores, an integral rear wall closing said central suction space on one end of said cylinder housing, an integral front wall on the other end thereof, said front and rear walls extending generally radially and including respective peripheral portions formed continuously therearound, means forming a suction inlet in said rear wall, a plate located within each of said bores having the peripheral edge thereof in engagement with each of said front and rear walls of said cylinder housing, an annular sheet metal closure member located in surrounding relationship to said cylinder housing having an inner surface thereon maintained in juxtaposed relationship with the surfaces of the continuously formed peripheral portions of said rear wall and said front wall, means for retaining said sheet metal closure member on said cylinder housing, means for sealing between said cylinder housing and said sheet metal closure member completely circumferentially therearound to define an annular high pressure discharge space formed radially outwardly of each of said cross bores and each of said cross bores communicating with said discharge space, said cylinder housing having circumferentially located radially inwardly formed wall cutouts therein in communication with said discharge space to define circumferentially spaced discharge muffler cavities between said front and rear walls of said cylinder housing, said plate engaging the front and rear walls of said housing at said wall cutouts, means forming a discharge opening in said cylinder housing rear wall in communication with said high pressure discharge space for communicating each of said circumferentially spaced discharge muffler cavities with the outside of said compressor, a piston in each of said cross bores, means including an integral eccentrically offset rotary drive shaft in said central suction space for reciprocating each of said pistons within said cross bores, suction valve means on each of said pistons for drawing gas from said suction inlet through said suction space into each of said cross bores, discharge valve means on said plate for directing compressed gas from each of said cross bores into said annular high pressure discharge space.
3. A compressor having an integral cylinder housing with four cross bores therein intersecting in a common plane, said cylinder housing having a centrally located suction cavity therein, an exterior rear cylinder wall closing one end of said central suction cavity, a front cylinder wall having a central opening therein, said rear cylinder wall having a centrally located inwardly directed axial hub thereon, a bore within said hub defining a first bearing, means defining a bearing housing located outwardly of said cylinder housing front wall including a bore therein defining a second bearing in alignment with said first bearing, an integral drive shaft having first and second journal portions thereon supported respectively in said first bore and said second bore, a shaFt portion between said first and second journal portions located eccentrically with respect thereto and in said central suction cavity, an inclined shaft portion on each end of said eccentric shaft portion integrally connecting it with said first and second shaft journal portions for reducing the width between said journal portions and to locate main shaft bearings close to crank arm loads to reduce shaft moments, a slider block having a central opening therein located coaxially of said eccentric shaft portion in said central suction cavity, a plurality of separately insertable elongated round needles supported between said slider block opening and said eccentric shaft portion in said central suction cavity for rotatably supporting said slider block on said eccentric shaft portion, said needles constituting the sole bearing means between said eccentric shaft portion and said slider block opening, a first needle retainer element supported on said eccentric shaft portion and overlying said slider block opening to prevent axial movement of said needles, a second needle retainer element supported on said eccentric shaft portion to prevent axial movement of said needles in an opposite axial direction, a piston in each of said cylinder bores, a first yoke including an elongated slot therein in surrounding relationship to one of said inclined shaft portions to permit rotation thereof with respect to said first yoke, said first yoke having opposite ends thereon located on one side of a first pair of said pistons, said first yoke having an inside surface thereon in engagement with said needle retainer element to maintain separation from said slider block, means for securing said opposite yoke ends to the stem portions on each of said pistons for joining said first pair of pistons for concurrent reciprocation within said bores, a second yoke having an inner surface thereon in engagement with said second needle retainer element, said second needle retainer element to maintain separation of said second yoke from said slider block, said second yoke including an elongated opening therein around said second shaft inclined portion to permit rotation thereof with respect to said second yoke, said second yoke having opposite ends thereon located on one side of a second pair of said pistons, means for securing said opposite ends of said second yoke to stems of said second pair of pistons to join said second pair of pistons for concurrent reciprocation within said bores, means for rotating said shaft to cause said slider block to move axially with respect to said pistons, means coupling said slider block with said pistons to cause opposite reciprocation thereof into and out of said bores, valve means on said pistons for drawing gas from said central suction cavity into one end of each of said cylinder bores, discharge valve means at the opposite end of said cylinder bores to direct compressed gas from each of said cylinder bores, means including an inlet opening to said central suction cavity for directing return gas thereto, and means including an outlet opening to said cylinder housing for receiving high pressure gas from each of said cylinder bore discharge valve means.
4. A compressor including an integral cylinder housing having four cross bores located therein and intersecting in a common plane, a central suction cavity within said cylinder housing in communication with each of said cross bores, said cylinder housing having a rear wall closing one end of said suction cavity, said cylinder housing having a front wall at the other end of said suction cavity with an opening therein, a suction inlet in said rear wall for directing return gas into said suction cavity centrally of said cylinder housing, a first bearing on said rear housing, means defining a second bearing located in alignment with said first bearing at a point centrally of the opening in said front wall, a shaft having first and second journal portions thereon supported by said first and second bearings for rotation with reSpect thereto, a piston in each of said cylinder bores, drive means within said central suction cavity for exposure to said return gas and connecting said shaft to each of said pistons for causing opposite reciprocation of each of said pistons within said cross bores upon rotation of said shaft, a sheet metal closure having an annular peripheral segment thereon overlying the outer periphery of said cylinder housing to close each of said cross bores therein, each of said cross bores having a rigid member supported therein for reinforcing the front wall of said cylinder housing, said sheet metal closure having a front surface thereon engaged with said front wall of said cylinder housing at the reinforced portion, a conical surface on said closure member directed outwardly of said cylinder housing including a radially inwardly directed central portion thereon, said means defining a second bearing having a housing portion thereon secured to said radially inwardly directed portion of said closure member, means for maintaining a sealed relationship between said front wall of said cylinder housing and said front surface of said closure member and to secure said closure member on said cylinder housing completely around the outer periphery of said cylinder housing, said cylinder housing having wall means thereon forming a plurality of cut outs therein at circumferentially located spots therearound between each of said cylinder bores to define a plurality of discharge muffler cavities, said cylinder housing and said closure member defining a space communicating each of said cylinder bores with said circumferentially spaced muffler cavities, said rigid reinforcing member reinforcing said housing at each of said cavities, said sheet metal closure member including an inner surface thereon formed continuously around said cylinder housing, an annular seal in said cylinder housing in engagement with inner surface of said closure member to seal between the rear wall of said cylinder housing and said closure member, said rear wall having a clamp surface thereon formed axially inwardly and continuously therearound, said sheet metal closure member having an edge portion thereon bent over and into engagement with said inclined clamp surface to force the front surface of said closure member against the front wall of said cylinder housing and to clamp the circumferential portion of said closure member in sealing engagement with said annular seal, said bent over edge portion connecting with said inwardly directed continuously formed clamp surface of said rear wall to prevent separation of said closure member from said cylinder housing upon pressurization of the chamber formed therebetween.
5. A compressor for an automotive refrigeration system adapted to be operated at speeds up to 3000 revolutions per minute comprising a rigid cast single piece cylinder housing having generally circular front and rear walls defining therebetween four cross bores intersecting in a common plane, a central low pressure suction space within said cylinder housing communcating with each of said cross bores, said rear wall closing said central suction space on one end of said cylinder housing, means for closing said central suction space at the other end of said cylinder housing, means forming a suction port in said rear wall in communication with said suction space and adapted for connection with said refrigeration system, a retainer plate located within each of said bores and having the peripheral edge thereof in engagement with each of said front and rear walls of said cylinder housing, an annular sheet metal closure member located in surrounding relationship to said cylinder housing having an inner surface thereon in engagement with the outer periphery of said rear wall and said front wall, means for retaining said sheet metal closure member on said cylinder housing, means for sealing between said cylinder housing and said sheet metal closure member at their said engagement completely circumferentially therearound To define an annular high pressure discharge space formed radially outwardly of each of said cross bores, each of said cross bores communicating with said discharge space through its respective retainer plate, said cylinder housing having circumferentially located radially inwardly formed wall cutouts therein in communication with said discharge space to define circumferentially spaced discharge muffler cavities between said front and rear walls of said cylinder housing and between adjacent cylinder bores, each of said retainer plates engaging said housing at said wall cutouts to separate each of said cross bores from said discharge space at the point of communication therebetween, means forming a discharge port in said rear wall in communication with said discharge space and adapted for connection with said refrigeration system for placing all of said circumferentially spaced discharge muffler cavities in communication with said refrigeration system, piston means slidably supported by the inner surface of each of said cross bores, means including a bearing mounting in communication with said central suction space for reciprocating each of said piston means within its respective cross bore throughout the sliding movement of each of said piston means when said compressor is operated at said speeds up to 3000 revolutions per minute, suction valve means supported on each of said piston means for drawing low pressure gas from said suction port through said suction space into each of said cross bores, discharge valve means supported on each of said retainer plates for directing compressed high pressure gas from each of said cross bores into said annular high pressure discharge space.
6. A compressor comprising a rigid cast single piece cylinder housing with four cross bores formed in intersecting relation in a common plane therein between generally radially extending front and rear walls of the housing that include respective peripheral portions formed continuously therearound, said front wall including a central opening therein, a central suction space within said housing in communication with said front wall opening and each of said cross bores, a suction port in said rear wall for directing return gas into the central suction space, means including a discharge port in said rear wall for directing discharge gas from said cross bores, a piston located in each of said cross bores, a bearing hub in said rear wall located centrall thereof and in communication with said central suction space by lubricant bleed passageway means, means forming a bearing housing located coaxially of said bearing hub and said front wall opening and in communication with said central suction space by lubricant bleed passageway means, a shaft having generally solid first and second journal portions thereon rotatably supported respectively in said bearing hub and said bearing housing, a shaft eccentric portion located in the same plane as each of said cross bores and in said central suction space, inclined intermediate shaft portions located in the same plane as each of said cross bores and integrally connecting each of said shaft journal portions with said shaft eccentric portion for locating main shaft bearing points close to crank arm loads to reduce shaft moments, each of said inclined shaft portions having a connection surface thereon offset from the longitudinal axis of said first and second shaft journal portions, a first counterweight having a leg portion thereon in engagement with the connection surface on one of said inclined shaft portions, means for fixedly securing said first counterweight leg portion to said connection surface thereof, said first counterweight having a radially outwardly located offset portion thereon located axially outwardly of said one of said inclined shaft portions at a point radially outwardly of said bearing hub, a second counterweight having a leg portion thereon in engagement with the connection surface on the other inclined shaft portion, means for fixedly Securing said second counterweight leg portion to said last-mentioned connection surface, said second counter-weight having a radially outwardly located offset portion thereon located axially outwardly of said other inclined shaft portion at a point radially outwardly of said bearing housing, drive means in said central suction space between said shaft eccentric portion and said pistons for causing reciprocation of said pistons within said cross bores upon rotation of said shaft, the jointure between said shaft eccentric portion and said drive means being in said central suction space and exposed to said return gas, said first and second counterweights serving to balance the inertia of said offset shaft eccentric portion and said inclined intermediate shaft portions and said drive means during operation of said compressor.
7. The compressor of claim 6 wherein said jointure contains a plurality of separately insertable needles engageable on one side thereof with said shaft eccentric portion and engageable on the other side thereof with said drive means, said needles constituting the sole bearing means between said eccentric portion and said drive means.
8. A radial compressor comprising a rigid cast single-piece cylinder housing having four cross bores which are disposed in radial cylinder portions of the housing and intersect in a common plane between generally radially extending front and exterior rear walls of the housing that include respective peripheral portions formed continuously theraround, said housing having discharge regions at the radially outer ends of the respective cross bores and a central suction space in communication with the radially inner ends of said respective cross bores, said central suction space being defined on one side by the rear wall of said housing and on the other side by a central opening in the front wall of said housing, said housing having spaces circumferentially between adjacent cylinder portions of the housing forming muffler cavities which are in communication with said discharge regions but are sealed off by wall portions of the cylinder housing from said central suction space, an exterior annular sheet metal closure member retained on the cylinder housing in a position surrounding the cross bores and having an inner surface maintained in sealing relationship with surfaces of the continuously formed peripheral portions of the front and rear walls of the cylinder housing to thereby define an annular high pressure discharge space disposed radially outwardly of the cross bores and in communication with said discharge regions of the cross bores and with said muffler cavities, a generally annular bearing support member closing said central opening in the front wall and forming, in conjunction with a bearing hub that is formed centrally in the rear wall and integral therewith, a bearing mounting for a rotary drive shaft in communication with said central suction space, a plurality of apertured pistons slidably mounted within the respective cross bores, a rotary drive shaft in said bearing mounting adapted to effect reciprocation of said pistons within said respective cross bores, an apertured rigid valve plate located within each of the cross bores radially outwardly of the respective piston, with a peripheral edge of each valve plate in engagement with the front and rear walls of the cylinder housing, an intake aperture extending to the central suction space of the cylinder housing, an intake valve on each of the pistons effective, on reciprocation of the piston, to allow gas to pass from the central suction space into a compressive space within the cross bore between the respective piston and valve plate, a discharge valve on each of the valve plates effective, on reciprocation of the respective piston, to supply compressed gas from the respective compressive space to the annular high pressure discharge space, and a discharge aperture extending from the annular high pressure discharge space of the cylinder housing to the outside of the coMpressor.
9. The radial compressor of claim 8 wherein said intake aperture and said discharge aperture extend through said rear wall.
10. The radial compressor of claim 8 wherein the adaptation of said rotary drive shaft to effect reciprocation of said pistons includes as integral portions of the shaft two inclined shaft portions with a shaft eccentric portion therebetween, a slider block having a bore around said eccentric portion, a plurality of separately insertable needles between and in engagement with the outer periphery of said eccentric portion and the bore of said slider block and needle retainer means to prevent said needles from moving axially outwardly of the bore of said slider block, said needles constituting the sole bearing means between said eccentric portion and the bore of said slider block.
11. The compressor of claim 10 wherein the front to rear length thereof from said bearing support member to the rear wall of said cylinder housing is substantially equal to the width and height of said compressor at the peripheral portions of said front and rear walls of said cylinder housing, thereby to provide a highly compact cubical configuration for said compressor.
US00254511A 1972-05-18 1972-05-18 Radial compressor with two-piece cylinder housing and shell Expired - Lifetime US3784331A (en)

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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3871793A (en) * 1973-12-28 1975-03-18 Jr John W Olson Automotive refrigeration compressor module
US4352640A (en) * 1979-02-24 1982-10-05 Honda Giken Kogyo Kabushiki Kaisha Fluid compressor
US4474541A (en) * 1983-06-10 1984-10-02 Tecumseh Products Company Internal crankcase support for a radial compressor
US4721443A (en) * 1987-03-16 1988-01-26 Tecumseh Products Company Discharge valve retainer for a compressor
US5180291A (en) * 1992-04-27 1993-01-19 General Motors Corporation Pulsating oil injector for radial refrigerant compressor
US20160294251A1 (en) * 2015-03-31 2016-10-06 Kabushiki Kaisha Toyota Jidoshokki Electric compressor
US20180195503A1 (en) * 2017-01-11 2018-07-12 Bristol Compressors International, Llc Fluid compressor
WO2022238149A1 (en) * 2021-05-10 2022-11-17 thyssenkrupp Presta Ilsenburg GmbH Radial piston pump, in particular radial piston compressor
WO2022238148A1 (en) * 2021-05-10 2022-11-17 thyssenkrupp Presta Ilsenburg GmbH Radial piston pump, and process for manufacturing a radial piston pump

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Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3871793A (en) * 1973-12-28 1975-03-18 Jr John W Olson Automotive refrigeration compressor module
US4352640A (en) * 1979-02-24 1982-10-05 Honda Giken Kogyo Kabushiki Kaisha Fluid compressor
US4474541A (en) * 1983-06-10 1984-10-02 Tecumseh Products Company Internal crankcase support for a radial compressor
US4721443A (en) * 1987-03-16 1988-01-26 Tecumseh Products Company Discharge valve retainer for a compressor
US5180291A (en) * 1992-04-27 1993-01-19 General Motors Corporation Pulsating oil injector for radial refrigerant compressor
US20160294251A1 (en) * 2015-03-31 2016-10-06 Kabushiki Kaisha Toyota Jidoshokki Electric compressor
US20180195503A1 (en) * 2017-01-11 2018-07-12 Bristol Compressors International, Llc Fluid compressor
WO2018132591A1 (en) * 2017-01-11 2018-07-19 Bristol Compressors International, Llc Fluid compressor
WO2022238149A1 (en) * 2021-05-10 2022-11-17 thyssenkrupp Presta Ilsenburg GmbH Radial piston pump, in particular radial piston compressor
WO2022238148A1 (en) * 2021-05-10 2022-11-17 thyssenkrupp Presta Ilsenburg GmbH Radial piston pump, and process for manufacturing a radial piston pump

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