CA2063942C - Integral suction system - Google Patents
Integral suction systemInfo
- Publication number
- CA2063942C CA2063942C CA 2063942 CA2063942A CA2063942C CA 2063942 C CA2063942 C CA 2063942C CA 2063942 CA2063942 CA 2063942 CA 2063942 A CA2063942 A CA 2063942A CA 2063942 C CA2063942 C CA 2063942C
- Authority
- CA
- Canada
- Prior art keywords
- suction
- cylinder
- motor
- cylinder head
- cylinders
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/06—Cooling; Heating; Prevention of freezing
-
- 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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
- F04B39/123—Fluid connections
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
Abstract
A gas flow system for a hermetic compressor is described which reduces the transfer of heat from the cylinder head and the hot discharge gases along with other hot internal compressor parts, wherein a separately formed suction tube is made from a low thermal conductivity plastic and is adapted to be received in a separately formed cylinder head. The cylinder head includes discharge chambers formed integrally therein but is adapted to receive the suction tube, while the suction tube includes a conduit defining a suction plenum having a suction inlet and adjutages extending transverse to the conduit which extend to the valve plate and communicate with openings in the cylinder head in order that the refrigerant flowing therein bypass the hot cylinder head and flows directly into the cylinder. The gas flow system also provides cooling for the motor in which a part of the refrigerant which flows into the suction tube is directed through the motor.
Grooves formed in the cylinder head walls accommodate O-rings that allow a press fit of the suction tube onto the cylinder head.
Grooves formed in the cylinder head walls accommodate O-rings that allow a press fit of the suction tube onto the cylinder head.
Description
` ~ 20639~2 The present invention relates to hermetic ssors and, more particularly, to a suction system for a hermetic ~ essor.
Hermetic compressors are utilized for circulating a refrigerant gas through a closed refrigerant system. In operation, the refrigerant vapor is fed into the interior of the ~ _ essor through an intake pipe in the sealed housing defining the compressor. Once inside the ~ssor, the refrigerant vapor is introduced into a ~ essuL cylinder wherein the vapor s , ~ssed by a piston within the cylinder resulting in an increase in temperature. The vapor exits the cylinder through an exhaust valve, consequently f lowing into the discharge portion of the compressor to circulate through the external refrigerant system to return to the ~ ~ssor unit .
Present practice requires that the design of ,- essors be as compact as possible, thus the limited available space within the ~ ssor assembly imposes severe size constraints for the suction assembly as well as the discharge elements. Because of this, it is n~ cllary to extend the internal suction system elements, e.g.
muf f lers, conduits, cavities, in close proximity to other ~ I essor parts that generate and transmit heat.
In the design of high efficiency compressors it is also important to reduce or eliminate noise generated by the suction process. In this regard, 60me hermetic motor compressors employ a shroud over the open end of the motor assembly to attenuate suction noise generated by pressure pulsations produced by the compressor .
Hermetic compressors are utilized for circulating a refrigerant gas through a closed refrigerant system. In operation, the refrigerant vapor is fed into the interior of the ~ _ essor through an intake pipe in the sealed housing defining the compressor. Once inside the ~ssor, the refrigerant vapor is introduced into a ~ essuL cylinder wherein the vapor s , ~ssed by a piston within the cylinder resulting in an increase in temperature. The vapor exits the cylinder through an exhaust valve, consequently f lowing into the discharge portion of the compressor to circulate through the external refrigerant system to return to the ~ ~ssor unit .
Present practice requires that the design of ,- essors be as compact as possible, thus the limited available space within the ~ ssor assembly imposes severe size constraints for the suction assembly as well as the discharge elements. Because of this, it is n~ cllary to extend the internal suction system elements, e.g.
muf f lers, conduits, cavities, in close proximity to other ~ I essor parts that generate and transmit heat.
In the design of high efficiency compressors it is also important to reduce or eliminate noise generated by the suction process. In this regard, 60me hermetic motor compressors employ a shroud over the open end of the motor assembly to attenuate suction noise generated by pressure pulsations produced by the compressor .
2 ~ ~ 3 ~ ~ 2 In addition, it is necessary to limit or eliminate the transfer of heat from hot compressor parts such as the wall of the housing, the discharge system, the cylinder block, and the oil, to the relatively cooler intake gas. The intake gas must remain cool to facilitate ~ t:ssor operation, as overheated intake gas causes an increase in _ ~ssor work due to the lowering of the specif ic gravity of the intake gas reducing the amount of gas entering the cylinder chamber.
Various provisions have been made by the prior art to rectify these problems, such as an ~ ~ ,"
intake pipe for the motor _ ~ssor being directly connected to a suction muf f ler of a cylinder head, and within the sealed housing, the intake opening of the suction muffler or suction conduit being disposed as opposed to the tip end of the intake pipe at a minimum distance, or a muffler shell and conduit being formed from a plastic material of low thermal conductivity to minimize heat transfer to the suction gas. Bypass suction conduits, often equipped with the suction mufflers, have also been provided to give continuous unrestricted fluid passageway for suction gas from the motor shroud or from the intake pipe to the suction cavities in the cylinder head. .!.. 1.
Commonly, compressor cylinder heads for hs~n-ll inq the gas flow for both the discharge and suction sides are manufactured from cast iron or aluminum to provided side-by-side or adjacent suction and discharge cavities separated by dividing walls which were preferably made as thin as possible to allow a maximum suction and aischarge plenum volume in the limited amount o~
available space. In addition, some efforts to 2~63942 overcome the overheating of the suction gas in the cylinder head suction plenum have resulted in tubular liners fabricated from a low thermal conductivity plastic preventing heat transfer to the suction gas, eliminating the suction plenum in the cylinder head and attaching a suction conduit to the relatively thin valve plate, or manufacturing the suction muffler out of a low thermal conductivity plastic. Further arrangements have included ut; l; ~ i ng separate - -discharge and suction cylinder heads for the discharge and suction chambers while the suction cylinder head is formed of a plastic material of low thermal conductivity to minimize heat transfer between the suction and discharge cylinder heads. `~
}iowever, even with these modifications, the compressors in the prior art are often not acceptable because of various disadvantages such that the transmission of vibration from the compressor to the eYternal piping was increased and that prevention of overheating of the suction gas in the suction cavities of the cylinder head was not sufficient. In addition, these modif ications have increased restrictions on the flow of suction gas at the suction port because of the reduced cross-sectional area or the lack of an immediately adjacent suction plenum, also consequently increasing the noise level.
For larger refrigeration and air conditioning 30` ` single and multi cylinder ' essors, such modifications are often not acceptable because of certain disadvantages such as complexity, dimensions of the suction system and discharge system with larger contact areas for the materials with different coefficients of expansion due to heat, limited space, higher oscillation forces of 2~63~2 the suction system element due to pressure pulsations, dif f iculties on assembly, and higher costs.
The present invention provides, in a compressor, a one-piece integral suction adaptor A~ aAting suction porting while defining a suction plenum, disposed on a cylinder head defining separate discharge l~.h~ . and porting, which draws suction gas from the interior of the compressor housing. The suction adaptor also includes suction porting communicating with a passage in the cylinder block allowing gas to f low through the motor to effect cooling thereof while providing a continuous circulating flow of refrigerant gas into the integral suction adaptor.
The present invention, in one form thereof, provides a one-piece integral suction adaptor disposed on the cylinder head in which a main portion of the refrigerant gas is drawn from the interior of the ~ es~or housing located in the close proximity of the compressor housing intake pipe, or int~ - ';Ate suction muffler between the intake pipe and the integral suction adaptor, while another portion of the refrigerant gas is drawn through the motor rotor-stator gap to effect cooling of the motor thereof.
The integral suction adaptor is constructed such that there is a continuous f low of the 3 0 refrigerant gas through the motor rotor-stator gap necessary for motor cooling, and this portion of rerrigerant gas combined with the main portion of the refrigerant gas is delivered to one of the cylinders without contacting any hot surface of the cylinder head or other parts. The integral suctivn adaptor is preferably made from plastic to ` 2~3~2 ~ .
reduee the tran6fer of heat from the eompressor parts and walls of the housing to the intake refrigerant gas. The exterior walls of the diseharge cavities of the cylinder head adjaeent to the exterior walls of the suction plenums of the integral suction adaptor are spaced from each other to provide an additional thermal barrier and further reduce suction gas heating in the cavities and passage of the cylinder head and integral suction adaptor. O-rings are disposed in grooves within the space between the exterior walls of the discharge cavitie6 of the cylinder head and the exterior walls of the suction plenums of the integral suction adaptor allowing a press-fit ~oining of the integral suction adaptor onto the cylinder head providing vibration dampening while effeeting sealing.
A gas flow system eomprises a eylinder head disposed on the valve plate having walls defining 20 ~ a closed discharge ehamber, motor eooling means ~ ~, for eooling the motor by flowing refrigerant through said motor, and a low thermal conductivity suction tube def ining a suction plenum disposed on said eylinder head having a suetion inlet port in fluid eommunieation with the internal low pressure eavity, ineluding an elongate eonduit and a first adjutage extending through said eylinder suetion opening and extending to the valve plate (but not interfering with it) for bypassing the eylinder head, a motor flowthrough opening eommunieating with said internal low ~)LeS=iULe cavity and adapted to reeeive refrigerant from the motor eooling means .
It is thus an objeet of the present invention 35~ to minimize the transfer of heat from the diseharge eavities in a eylinder head having 20S3~42 di6charge plenums formed integrally therein and separated by internal walls to the suction plenums of the integral suction adaptor and refrigerant gas entering therein.
It is further an object of the present invention to combine delivery of the refrigerant gas intended to cool the motor and the suction gas delivered to the cylinder suction chamber from the j ~, interior of the ~_ es60r housing located in the close proximity of the intake pipe.
It is still further an object of the present invention to minimize the transfer of heat to the suction gas from all internal ~ ~:ssor parts.
The above mentioned and other f eatures and objects of this invention, and the manner of attaining them, will become more apparent and the invention itself will be better understood by reference to the following description of embodiments of the invention taken in conjunction with the accompanying drawings, wherein:
FIG. 1 is an elevational view, partly in 6ection, of a compressor incorporating a pref erred ho.~ of the present invention;
FIG. 2 i8 an elevational sectional view of a compressor incorporating a preferred embodiment of the present invention taken along line 2--2 of FIG.
l;
FIG. 3 is a sectional view of the cylinder head and integral suction adaptor assembly of the 3 0 present invention taken along line 3 -3 of FIG . 4;
FIG. 4 is a bottom view of the cylinder head and integral suction adaptor assembly of the present invention;
FIG. 5 is a bottom view of the integral suction adaptor of the present invention; and 2~63~2 FIG. 6 is a side elevational view of the integral suction adaptor of the pre6ent invention.
Referring to the drawings, and in particular to FIGS. 1 and 2, there is shown a hermetically sealed, reciprocating piston compressor 10 embodying the present invention. C~ ~s50~ 10 includes a sealed compressor housing 12 encapsulating the L. -; nd~r of the ~ e:ssor cnrr~ nts and tl-'f ~ n; ng an internal, low pressure cavity 14. Disposed within housing 12 i5 a cylinder block 16 supporting a crankshaft 18 which is driven by a motor 20 which includes a stator 22 and rotor 24 each having windings thereon. Shock mounts 34 attached to cylinder block 16 and housing 12 suspend the i~_.. ressor components within housing 12.
By way of illustration, and without any limitation on the invention, orientation of compressor 10 in the illustrated preferred ~ ~;r ~ is with cylinder block 16 sl~r~n~l.od vertically beneath motor 20. However, other orientations of the ~ _ essor ~ ,..e1l1 s are contemplated and fall within the scope and spirit of the present invention.
Attached to crankshaft 18 within cylinder block 16 are crankpins 26 and 27, respectively connected to connecting rods 28 and 29, which are in turn respectively connected to pistons 3 o and 31, within respective cylinders 32 and 33. The lower end 36 of crankshaft 18 is radially :,ur~u~ded by bushing 38 in outboard bearing 40 which is f ixedly mounted to cylinder block 16 by bearing bolts 42.
A valve plate 44 is disposed on the end of cylinders 32 and 33 and supports the suction and discharge valving (not shown) to and from the 2~3~42 cylinders. Valve plate 44 includes a suction aperture 46 (Fig. 2) communicating with a cylinder block passage 48 adjacent stator 22 of motor 20.
Valve plate 44 also includes cylinder suction apertures 43 and 45 respectively communicating with cylinders 32 and 33. Cylinder block passage 48 communicates with stator/rotor cavity 50 and stator/rotor gap 52 to provide a continuous suction path through the stator/rotor gap 52 effecting cooling of motor 20 and providing an additional suction source. A cylinder head 54 is mounted over valve plate 44 separated by a gasket 5 6 . In accordance with the present invention, an ' ~ integral suction adaptor 58 (to be de6cribed ~h " " ' ' ' ~ ~' detail hereinbelow) is disposed on cylinder head 54 and is connected to suction muffler 60 by way of suction connector 62.
As best shown in FIGS. 3 and 4, integrally formed in cylinder head 54 are discharge cavities 64 and 65 which communicate with discharge port 66, discharge muffler 67, dlscharge tube 68, and outlet 69 (see FIG. 1). A ~J:eSt~ULe relief valve 70 ls also in communication with discharge cavities 64 and 65 should excess ~Les~uLe in cylinder head 54 require venting. In addition, integrally formed in cylinder head 54 are cylinder suction npC~n;n~c 72 and 73, and a rotor/stator flowthrough suction opening 74 separated from the high pressure discharge cavities 64 and 65 by cylindrical cylinder head walls 76, 77, and 78 respectively. Cylinder suction op~ni ngs 72 and 73 are disposed over cylinders 32 and 33, respectively, while rotor/stator flowthrough suction opening 74 is disposed over cylinder block passage 48 so as to allow 6uction gas entry flowing through motor 20. Formed ln the inside of 2~3g~2 cylinder head walls 76, 77, and 78 defining cylinder suction opPn; n~s 72 and 73, and rotor/stator suction opening 74 respectively, are respective circular grooves 80, 81, and 82 designed to respectively acc~ ~te 0-rings 84, 85, and 86 made of a refrigerant and oil resistant material such as polytetrafluoroethylene, although other known materials may be used. In addition, cylinder head 54 also includes bolt holes 88 in which bolts 89 (shown in FIG. l) are ac ' ted in order to secure cylinder head 54 to cylinder block 16.
In accordance with the present invention, and with additional reference to FIGS. 5 and 6, there is shown the integral suction adaptor 58 of the present invention. Integral suction adaptor 58 is made from a thPr~-l ly low cnn~ ct;vity plastic such as Nylon, or Valox,, although other known thPrr-l ly low conductivity plastics or materials may be utilized, in order to reduce the transfer of heat to the intake refrigerant gas from the compressor parts and walls of the housing.
Integral suction adaptor 58 includes suction connector 62 integral with a tubular-like conduit 90 defining a suction plenum. Along the longitudinal length of conduit 90 nearest suction connector 62 is a rotor/stator suction port 92 defined by a circular protruding wall 94 radially extending from conduit 90 and which is adapted to be received through rotor/stator suction opening 74 of cylinder head 54. Likewise, along the longitudinal length of conduit 90 are two cylinder intake ports 96 and 97 defined by adjutages 98 and 99 radially extending from conduit 90 and which are adapted to be respectively received through cylinder suction openings 72 and 73 of cylinder 2~63~
~ .
head 54. It i5 to be noted, however, that the integral suction adaptor 58 cam be modified to accommodate a one cylinder ~ a~sv~ by having only one cylinder intake port def ined by one ad j utage .
As best shown in FIG. 3, integral suction adaptor 58 is coupled to cylinder head 54 by fitting the radially extending ports 92, 96, and 97, which preferably extend (but not interfere) substantially to the surface 49 of valve plate 44, respectively into rotor/stator suction opening 74 and cylinder intake ports 96 and 97, being held into place by 0-rings 86, 84, and 85. By reason of the resilience of the o-rings, the integral suction adaptor 58 can be slightly displaced to all sides in a plane perpendicular to the axes of cylinders 32 and 33. This connection feature also facilitates assembly because the integral suction adaptor 58 can be pushed in the cylinder head openings. In addition to the retention characteristics of the 0-rings, the integral suction adaptor 58 can also be strapped across the cylinder head. The 0-rings also act as damping elements which oppose the transmis~ion o~ sounds and vibrations from cylinder head 54 to the thinner wall of the integral suction adaptor 58.
In addition, the 0-rings work as sealing elements which separate the interior of the rotor/stator suction port and the cylinder intake ports from the interior ~ OL cavity 14.
During operation of compressor 10, refrigerant enters housing 12 through inlet pipe 100. Because inlet pipe 100 opens into interior ~ ~ cavity 14 of housing 12, the ~ es~vL 10 of FIGS. 1 and 2 is a low back pressure compressor operating at suction pressure. The direction of 11 2~639~2 refrigerant f low is depicted by arrows . The main portion of the intake refrigerant gas is drawn into suction muffler 60 and into plenum conduit 90 which is in fluid communication with cylinder intake ports 96 and 97 which are respectively arranged over and in fluid communication with `~ ` cylinders 32 and 33 . In addition, since integral `~
suction adaptor is in f luid communication with cylinder block passage 48 via suction aperture 46 in valve plate 44 and rotor/stator suction port 72 of the integral suction adaptor 58, a portion of the refrigerant gas is drawn through the stator/rotor gap 52 into the stator/rotor cavity 50 to effect nP~C~ ry cooling of motor 20, which also provides a continuous flow of refrigerant gas into plenum conduit 90 of the integral suction adaptor 58.
It will be appreciated that the foregoing description of a preferred iL ' _ ';T' I of the present invention along with an alternative embodiment thereof, is presented by way of illustration only, and not by way of any limitation, and that various alternatives and modif ications may be made to the illustrated embodiment without departing from the spirit and scope of the invention.
, ~
Various provisions have been made by the prior art to rectify these problems, such as an ~ ~ ,"
intake pipe for the motor _ ~ssor being directly connected to a suction muf f ler of a cylinder head, and within the sealed housing, the intake opening of the suction muffler or suction conduit being disposed as opposed to the tip end of the intake pipe at a minimum distance, or a muffler shell and conduit being formed from a plastic material of low thermal conductivity to minimize heat transfer to the suction gas. Bypass suction conduits, often equipped with the suction mufflers, have also been provided to give continuous unrestricted fluid passageway for suction gas from the motor shroud or from the intake pipe to the suction cavities in the cylinder head. .!.. 1.
Commonly, compressor cylinder heads for hs~n-ll inq the gas flow for both the discharge and suction sides are manufactured from cast iron or aluminum to provided side-by-side or adjacent suction and discharge cavities separated by dividing walls which were preferably made as thin as possible to allow a maximum suction and aischarge plenum volume in the limited amount o~
available space. In addition, some efforts to 2~63942 overcome the overheating of the suction gas in the cylinder head suction plenum have resulted in tubular liners fabricated from a low thermal conductivity plastic preventing heat transfer to the suction gas, eliminating the suction plenum in the cylinder head and attaching a suction conduit to the relatively thin valve plate, or manufacturing the suction muffler out of a low thermal conductivity plastic. Further arrangements have included ut; l; ~ i ng separate - -discharge and suction cylinder heads for the discharge and suction chambers while the suction cylinder head is formed of a plastic material of low thermal conductivity to minimize heat transfer between the suction and discharge cylinder heads. `~
}iowever, even with these modifications, the compressors in the prior art are often not acceptable because of various disadvantages such that the transmission of vibration from the compressor to the eYternal piping was increased and that prevention of overheating of the suction gas in the suction cavities of the cylinder head was not sufficient. In addition, these modif ications have increased restrictions on the flow of suction gas at the suction port because of the reduced cross-sectional area or the lack of an immediately adjacent suction plenum, also consequently increasing the noise level.
For larger refrigeration and air conditioning 30` ` single and multi cylinder ' essors, such modifications are often not acceptable because of certain disadvantages such as complexity, dimensions of the suction system and discharge system with larger contact areas for the materials with different coefficients of expansion due to heat, limited space, higher oscillation forces of 2~63~2 the suction system element due to pressure pulsations, dif f iculties on assembly, and higher costs.
The present invention provides, in a compressor, a one-piece integral suction adaptor A~ aAting suction porting while defining a suction plenum, disposed on a cylinder head defining separate discharge l~.h~ . and porting, which draws suction gas from the interior of the compressor housing. The suction adaptor also includes suction porting communicating with a passage in the cylinder block allowing gas to f low through the motor to effect cooling thereof while providing a continuous circulating flow of refrigerant gas into the integral suction adaptor.
The present invention, in one form thereof, provides a one-piece integral suction adaptor disposed on the cylinder head in which a main portion of the refrigerant gas is drawn from the interior of the ~ es~or housing located in the close proximity of the compressor housing intake pipe, or int~ - ';Ate suction muffler between the intake pipe and the integral suction adaptor, while another portion of the refrigerant gas is drawn through the motor rotor-stator gap to effect cooling of the motor thereof.
The integral suction adaptor is constructed such that there is a continuous f low of the 3 0 refrigerant gas through the motor rotor-stator gap necessary for motor cooling, and this portion of rerrigerant gas combined with the main portion of the refrigerant gas is delivered to one of the cylinders without contacting any hot surface of the cylinder head or other parts. The integral suctivn adaptor is preferably made from plastic to ` 2~3~2 ~ .
reduee the tran6fer of heat from the eompressor parts and walls of the housing to the intake refrigerant gas. The exterior walls of the diseharge cavities of the cylinder head adjaeent to the exterior walls of the suction plenums of the integral suction adaptor are spaced from each other to provide an additional thermal barrier and further reduce suction gas heating in the cavities and passage of the cylinder head and integral suction adaptor. O-rings are disposed in grooves within the space between the exterior walls of the discharge cavitie6 of the cylinder head and the exterior walls of the suction plenums of the integral suction adaptor allowing a press-fit ~oining of the integral suction adaptor onto the cylinder head providing vibration dampening while effeeting sealing.
A gas flow system eomprises a eylinder head disposed on the valve plate having walls defining 20 ~ a closed discharge ehamber, motor eooling means ~ ~, for eooling the motor by flowing refrigerant through said motor, and a low thermal conductivity suction tube def ining a suction plenum disposed on said eylinder head having a suetion inlet port in fluid eommunieation with the internal low pressure eavity, ineluding an elongate eonduit and a first adjutage extending through said eylinder suetion opening and extending to the valve plate (but not interfering with it) for bypassing the eylinder head, a motor flowthrough opening eommunieating with said internal low ~)LeS=iULe cavity and adapted to reeeive refrigerant from the motor eooling means .
It is thus an objeet of the present invention 35~ to minimize the transfer of heat from the diseharge eavities in a eylinder head having 20S3~42 di6charge plenums formed integrally therein and separated by internal walls to the suction plenums of the integral suction adaptor and refrigerant gas entering therein.
It is further an object of the present invention to combine delivery of the refrigerant gas intended to cool the motor and the suction gas delivered to the cylinder suction chamber from the j ~, interior of the ~_ es60r housing located in the close proximity of the intake pipe.
It is still further an object of the present invention to minimize the transfer of heat to the suction gas from all internal ~ ~:ssor parts.
The above mentioned and other f eatures and objects of this invention, and the manner of attaining them, will become more apparent and the invention itself will be better understood by reference to the following description of embodiments of the invention taken in conjunction with the accompanying drawings, wherein:
FIG. 1 is an elevational view, partly in 6ection, of a compressor incorporating a pref erred ho.~ of the present invention;
FIG. 2 i8 an elevational sectional view of a compressor incorporating a preferred embodiment of the present invention taken along line 2--2 of FIG.
l;
FIG. 3 is a sectional view of the cylinder head and integral suction adaptor assembly of the 3 0 present invention taken along line 3 -3 of FIG . 4;
FIG. 4 is a bottom view of the cylinder head and integral suction adaptor assembly of the present invention;
FIG. 5 is a bottom view of the integral suction adaptor of the present invention; and 2~63~2 FIG. 6 is a side elevational view of the integral suction adaptor of the pre6ent invention.
Referring to the drawings, and in particular to FIGS. 1 and 2, there is shown a hermetically sealed, reciprocating piston compressor 10 embodying the present invention. C~ ~s50~ 10 includes a sealed compressor housing 12 encapsulating the L. -; nd~r of the ~ e:ssor cnrr~ nts and tl-'f ~ n; ng an internal, low pressure cavity 14. Disposed within housing 12 i5 a cylinder block 16 supporting a crankshaft 18 which is driven by a motor 20 which includes a stator 22 and rotor 24 each having windings thereon. Shock mounts 34 attached to cylinder block 16 and housing 12 suspend the i~_.. ressor components within housing 12.
By way of illustration, and without any limitation on the invention, orientation of compressor 10 in the illustrated preferred ~ ~;r ~ is with cylinder block 16 sl~r~n~l.od vertically beneath motor 20. However, other orientations of the ~ _ essor ~ ,..e1l1 s are contemplated and fall within the scope and spirit of the present invention.
Attached to crankshaft 18 within cylinder block 16 are crankpins 26 and 27, respectively connected to connecting rods 28 and 29, which are in turn respectively connected to pistons 3 o and 31, within respective cylinders 32 and 33. The lower end 36 of crankshaft 18 is radially :,ur~u~ded by bushing 38 in outboard bearing 40 which is f ixedly mounted to cylinder block 16 by bearing bolts 42.
A valve plate 44 is disposed on the end of cylinders 32 and 33 and supports the suction and discharge valving (not shown) to and from the 2~3~42 cylinders. Valve plate 44 includes a suction aperture 46 (Fig. 2) communicating with a cylinder block passage 48 adjacent stator 22 of motor 20.
Valve plate 44 also includes cylinder suction apertures 43 and 45 respectively communicating with cylinders 32 and 33. Cylinder block passage 48 communicates with stator/rotor cavity 50 and stator/rotor gap 52 to provide a continuous suction path through the stator/rotor gap 52 effecting cooling of motor 20 and providing an additional suction source. A cylinder head 54 is mounted over valve plate 44 separated by a gasket 5 6 . In accordance with the present invention, an ' ~ integral suction adaptor 58 (to be de6cribed ~h " " ' ' ' ~ ~' detail hereinbelow) is disposed on cylinder head 54 and is connected to suction muffler 60 by way of suction connector 62.
As best shown in FIGS. 3 and 4, integrally formed in cylinder head 54 are discharge cavities 64 and 65 which communicate with discharge port 66, discharge muffler 67, dlscharge tube 68, and outlet 69 (see FIG. 1). A ~J:eSt~ULe relief valve 70 ls also in communication with discharge cavities 64 and 65 should excess ~Les~uLe in cylinder head 54 require venting. In addition, integrally formed in cylinder head 54 are cylinder suction npC~n;n~c 72 and 73, and a rotor/stator flowthrough suction opening 74 separated from the high pressure discharge cavities 64 and 65 by cylindrical cylinder head walls 76, 77, and 78 respectively. Cylinder suction op~ni ngs 72 and 73 are disposed over cylinders 32 and 33, respectively, while rotor/stator flowthrough suction opening 74 is disposed over cylinder block passage 48 so as to allow 6uction gas entry flowing through motor 20. Formed ln the inside of 2~3g~2 cylinder head walls 76, 77, and 78 defining cylinder suction opPn; n~s 72 and 73, and rotor/stator suction opening 74 respectively, are respective circular grooves 80, 81, and 82 designed to respectively acc~ ~te 0-rings 84, 85, and 86 made of a refrigerant and oil resistant material such as polytetrafluoroethylene, although other known materials may be used. In addition, cylinder head 54 also includes bolt holes 88 in which bolts 89 (shown in FIG. l) are ac ' ted in order to secure cylinder head 54 to cylinder block 16.
In accordance with the present invention, and with additional reference to FIGS. 5 and 6, there is shown the integral suction adaptor 58 of the present invention. Integral suction adaptor 58 is made from a thPr~-l ly low cnn~ ct;vity plastic such as Nylon, or Valox,, although other known thPrr-l ly low conductivity plastics or materials may be utilized, in order to reduce the transfer of heat to the intake refrigerant gas from the compressor parts and walls of the housing.
Integral suction adaptor 58 includes suction connector 62 integral with a tubular-like conduit 90 defining a suction plenum. Along the longitudinal length of conduit 90 nearest suction connector 62 is a rotor/stator suction port 92 defined by a circular protruding wall 94 radially extending from conduit 90 and which is adapted to be received through rotor/stator suction opening 74 of cylinder head 54. Likewise, along the longitudinal length of conduit 90 are two cylinder intake ports 96 and 97 defined by adjutages 98 and 99 radially extending from conduit 90 and which are adapted to be respectively received through cylinder suction openings 72 and 73 of cylinder 2~63~
~ .
head 54. It i5 to be noted, however, that the integral suction adaptor 58 cam be modified to accommodate a one cylinder ~ a~sv~ by having only one cylinder intake port def ined by one ad j utage .
As best shown in FIG. 3, integral suction adaptor 58 is coupled to cylinder head 54 by fitting the radially extending ports 92, 96, and 97, which preferably extend (but not interfere) substantially to the surface 49 of valve plate 44, respectively into rotor/stator suction opening 74 and cylinder intake ports 96 and 97, being held into place by 0-rings 86, 84, and 85. By reason of the resilience of the o-rings, the integral suction adaptor 58 can be slightly displaced to all sides in a plane perpendicular to the axes of cylinders 32 and 33. This connection feature also facilitates assembly because the integral suction adaptor 58 can be pushed in the cylinder head openings. In addition to the retention characteristics of the 0-rings, the integral suction adaptor 58 can also be strapped across the cylinder head. The 0-rings also act as damping elements which oppose the transmis~ion o~ sounds and vibrations from cylinder head 54 to the thinner wall of the integral suction adaptor 58.
In addition, the 0-rings work as sealing elements which separate the interior of the rotor/stator suction port and the cylinder intake ports from the interior ~ OL cavity 14.
During operation of compressor 10, refrigerant enters housing 12 through inlet pipe 100. Because inlet pipe 100 opens into interior ~ ~ cavity 14 of housing 12, the ~ es~vL 10 of FIGS. 1 and 2 is a low back pressure compressor operating at suction pressure. The direction of 11 2~639~2 refrigerant f low is depicted by arrows . The main portion of the intake refrigerant gas is drawn into suction muffler 60 and into plenum conduit 90 which is in fluid communication with cylinder intake ports 96 and 97 which are respectively arranged over and in fluid communication with `~ ` cylinders 32 and 33 . In addition, since integral `~
suction adaptor is in f luid communication with cylinder block passage 48 via suction aperture 46 in valve plate 44 and rotor/stator suction port 72 of the integral suction adaptor 58, a portion of the refrigerant gas is drawn through the stator/rotor gap 52 into the stator/rotor cavity 50 to effect nP~C~ ry cooling of motor 20, which also provides a continuous flow of refrigerant gas into plenum conduit 90 of the integral suction adaptor 58.
It will be appreciated that the foregoing description of a preferred iL ' _ ';T' I of the present invention along with an alternative embodiment thereof, is presented by way of illustration only, and not by way of any limitation, and that various alternatives and modif ications may be made to the illustrated embodiment without departing from the spirit and scope of the invention.
, ~
Claims (13)
1. In a hermetic reciprocating piston compressor including a housing, an internal low pressure cavity defined by the housing, a cylinder block, a crankshaft, a valve plate disposed on said cylinder block, a motor having a rotor and a stator, and a cylinder in said cylinder block having a piston therein that reciprocates in an axial direction, a gas flow system comprising:
cylinder head disposed on the valve plate axially outwardly of the cylinder, said cylinder head having walls defining a closed discharge chamber in fluid communication with the cylinder and a discharge port in fluid communication with said discharge chamber, a cylinder suction opening axially outwardly disposed of the cylinder; motor cooling means for cooling the motor by flowing refrigerant through said motor; a low thermal conductivity suction tube defining a suction plenum disposed on said cylinder head having a suction inlet in fluid communication with the internal low pressure cavity, said suction tube including a conduit extending transverse to the axial direction of said cylinder, a first adjutage extending transverse to said conduit and extending through said cylinder suction opening, a motor flowthrough opening communicating with said internal low pressure cavity and adapted to receive refrigerant from said motor cooling means, said first adjutage extending substantially to said valve plate for substantially bypassing said cylinder head whereby the refrigerant flows directly to the cylinder.
cylinder head disposed on the valve plate axially outwardly of the cylinder, said cylinder head having walls defining a closed discharge chamber in fluid communication with the cylinder and a discharge port in fluid communication with said discharge chamber, a cylinder suction opening axially outwardly disposed of the cylinder; motor cooling means for cooling the motor by flowing refrigerant through said motor; a low thermal conductivity suction tube defining a suction plenum disposed on said cylinder head having a suction inlet in fluid communication with the internal low pressure cavity, said suction tube including a conduit extending transverse to the axial direction of said cylinder, a first adjutage extending transverse to said conduit and extending through said cylinder suction opening, a motor flowthrough opening communicating with said internal low pressure cavity and adapted to receive refrigerant from said motor cooling means, said first adjutage extending substantially to said valve plate for substantially bypassing said cylinder head whereby the refrigerant flows directly to the cylinder.
2. The gas flow system of claim 1, wherein said motor cooling means comprises: a suction passage formed in said cylinder block adjacent the stator, said suction passage in fluid communication with said motor flowthrough suction opening; and a rotor/stator gap defined by a space between the rotor and the stator, said gap in fluid communication with both the internal low pressure cavity and said suction passage.
3. The gas flow system of claim 1, wherein said motor flowthrough opening is in said cylinder head, and said suction tube further comprises a second adjutage extending transverse to said conduit and extending through said motor flowthrough opening.
4. The gas flow system of claim 1, wherein said suction tube is made from a thermally low conductivity plastic.
5. The gas flow system of claim 1, wherein said walls defining said cylinder suction opening and said motor flowthrough suction opening are each defined by a surface that includes a groove, wherein O-rings are disposed in said grooves.
6. In a hermetic reciprocating piston compressor for a refrigerant gas including a housing, an internal low pressure cavity defined by the housing, a cylinder block, a crankshaft, a valve plate disposed on said cylinder block, a motor having a stator and a rotor, and a plurality of parallel cylinders having a plurality of pistons disposed therein which reciprocate in an axial direction, a gas flow system comprising: a cylinder head disposed on the valve plate axially outwardly of the cylinders having a discharge port and a plurality of discharge chambers defined by walls, said discharge chambers corresponding to the number of cylinders, said discharge chambers in fluid communication with the cylinders and said discharge port, said walls also defining a plurality of cylinder suction openings axially outwardly disposed over the cylinders; motor cooling means for cooling the motor by flowing refrigerant through said motor; a low thermal conductivity suction tube defining a suction plenum disposed on said cylinder head having a suction inlet in fluid communication with the internal low pressure cavity, said suction tube including an elongate conduit extending transverse to the axial direction of said cylinders, a plurality of first adjutages corresponding to the number of cylinders, said adjutages extending transverse to said elongate conduit and extending through said plurality of cylinder suction openings, said plurality of first adjutages extending substantially to said valve plate for substantially bypassing said cylinder head whereby the refrigerant flows directly to the plurality of cylinders .
7 . The gas flow system of claim 6, wherein said suction tube is made from a thermally low conductivity plastic.
8 . The gas flow system of claim 6, wherein said suction tube includes a motor flowthrough opening communicating with said internal low pressure cavity and adapted to receive refrigerant from said motor cooling means.
9 . The gas flow system of claim 8, wherein said motor flowthrough opening is in said cylinder head, and said suction tube further comprising a second adjutage extending transverse to said elongate conduit and extending through said motor flowthrough opening .
10. The gas flow system of claim 6, wherein said walls defining said plurality of cylinder suction openings include grooves formed therein, wherein O-rings are disposed in said grooves.
11. In a hermetic reciprocating piston compressor for a refrigerant gas including a housing, a cylinder block, a crankshaft, a valve plate with a suction aperture and a plurality of cylinder suction apertures, a motor having a stator and a rotor, and a plurality of cylinders having a plurality of pistons disposed therein which reciprocate in an axial direction, a gas flow system comprising: a cylinder head disposed on the valve plate axially outwardly of the cylinders having a discharge port and a plurality of discharge chambers defined by integrally formed walls corresponding to the number of cylinders, said discharge chambers in fluid communication with the cylinders and said discharge port, said integrally formed walls also defining a plurality of cylinder suction openings axially outwardly disposed over the cylinders and defining a motor flowthrough suction opening in fluid communication with said suction aperture in said valve plate;
motor cooling means in the cylinder block for cooling the motor with the refrigerant gas, said motor cooling means in fluid communication with said suction aperture in said valve plate; and a low thermal conductivity suction tube defining a suction plenum disposed on said cylinder head having a suction inlet transverse to the axial direction of said cylinders, a plurality of first adjutages corresponding to the number of cylinders, said adjutages extending transverse to said elongate conduit and extending towards said plurality of cylinder suction openings, a second adjutage extending transverse to said elongate conduit and extending toward said motor flowthrough suction opening, said plurality of first adjutages extending substantially to said plurality of cylinder apertures in said valve plate for substantially bypassing said cylinder head whereby the refrigerant flows directly to the plurality of cylinders, said second adjutage extending substantially to said suction aperture in said valve plate whereby a portion of the refrigerant is received from the motor.
motor cooling means in the cylinder block for cooling the motor with the refrigerant gas, said motor cooling means in fluid communication with said suction aperture in said valve plate; and a low thermal conductivity suction tube defining a suction plenum disposed on said cylinder head having a suction inlet transverse to the axial direction of said cylinders, a plurality of first adjutages corresponding to the number of cylinders, said adjutages extending transverse to said elongate conduit and extending towards said plurality of cylinder suction openings, a second adjutage extending transverse to said elongate conduit and extending toward said motor flowthrough suction opening, said plurality of first adjutages extending substantially to said plurality of cylinder apertures in said valve plate for substantially bypassing said cylinder head whereby the refrigerant flows directly to the plurality of cylinders, said second adjutage extending substantially to said suction aperture in said valve plate whereby a portion of the refrigerant is received from the motor.
12. The gas flow system of claim 11, wherein said suction tube is made from a thermally low conductivity plastic.
13. The gas flow system of claim 11, wherein said walls defining said plurality of cylinder suction openings include grooves formed therein, wherein O-rings are disposed in said grooves.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US67695991A | 1991-03-28 | 1991-03-28 | |
| US07/676,959 | 1991-03-28 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CA2063942A1 CA2063942A1 (en) | 1992-09-29 |
| CA2063942C true CA2063942C (en) | 1996-09-10 |
Family
ID=24716725
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA 2063942 Expired - Fee Related CA2063942C (en) | 1991-03-28 | 1992-03-25 | Integral suction system |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP0505805B1 (en) |
| JP (1) | JPH05126050A (en) |
| BR (1) | BR9201009A (en) |
| CA (1) | CA2063942C (en) |
| DE (1) | DE69201580T2 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE69733402T2 (en) * | 1996-06-14 | 2006-04-27 | Matsushita Refrigeration Co., Higashiosaka | HERMETICALLY CAPSUED COMPRESSOR |
| US6457947B1 (en) | 1997-08-29 | 2002-10-01 | Luk Fahrzeug-Hydraulik Gmbh & Co. Kg | Piston compressor for refrigerant, with thermal insulation |
| KR102254862B1 (en) * | 2019-10-14 | 2021-05-24 | 엘지전자 주식회사 | Linear compressor |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS55150880A (en) * | 1979-05-11 | 1980-11-25 | Isao Muramatsu | Preparation of fish paste product containing fish eggs |
| DE2951463A1 (en) * | 1979-12-20 | 1981-07-02 | Copeland Corp., Sidney, Ohio | Refrigerator compressor induction conduit - has silencer to reduce noise integral with moulded plastics conduit |
| US4487555A (en) * | 1981-02-13 | 1984-12-11 | Mitsubishi Denki Kabushiki Kaisha | Hermetic motor compressor |
| JPS5868753A (en) * | 1981-10-21 | 1983-04-23 | Fuji Photo Film Co Ltd | Capsule toner |
| JPS6073072A (en) * | 1983-09-30 | 1985-04-25 | Toshiba Corp | Closed type compressor |
| JPH01121575A (en) * | 1987-11-02 | 1989-05-15 | Matsushita Refrig Co Ltd | Closed type electrically driven compressor |
-
1992
- 1992-03-09 EP EP19920103968 patent/EP0505805B1/en not_active Expired - Lifetime
- 1992-03-09 DE DE1992601580 patent/DE69201580T2/en not_active Expired - Fee Related
- 1992-03-24 BR BR9201009A patent/BR9201009A/en not_active IP Right Cessation
- 1992-03-25 CA CA 2063942 patent/CA2063942C/en not_active Expired - Fee Related
- 1992-03-30 JP JP10367692A patent/JPH05126050A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| JPH05126050A (en) | 1993-05-21 |
| EP0505805B1 (en) | 1995-03-08 |
| DE69201580D1 (en) | 1995-04-13 |
| EP0505805A3 (en) | 1992-11-25 |
| DE69201580T2 (en) | 1995-07-06 |
| BR9201009A (en) | 1992-11-24 |
| CA2063942A1 (en) | 1992-09-29 |
| EP0505805A2 (en) | 1992-09-30 |
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Legal Events
| Date | Code | Title | Description |
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| EEER | Examination request | ||
| MKLA | Lapsed |