US20140086760A1 - Compressor - Google Patents
Compressor Download PDFInfo
- Publication number
- US20140086760A1 US20140086760A1 US14/031,543 US201314031543A US2014086760A1 US 20140086760 A1 US20140086760 A1 US 20140086760A1 US 201314031543 A US201314031543 A US 201314031543A US 2014086760 A1 US2014086760 A1 US 2014086760A1
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- United States
- Prior art keywords
- wall
- cylinder block
- valve
- discharge
- bottom portion
- 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.)
- Abandoned
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Classifications
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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
- 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
-
- 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
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B1/141—Details or component parts
- F04B1/145—Housings
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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
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
-
- 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
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1045—Cylinders
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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
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1081—Casings, housings
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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
- 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
- F04B39/122—Cylinder block
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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
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/10—Valves; Arrangement of valves
Definitions
- the present invention relates to a compressor, and more particularly to a compressor including a cylinder block and a housing.
- Japanese Laid-Open Patent Publication No. 8-121330 describes a reciprocating compressor including single-headed pistons.
- the compressor includes a cylinder block having six bores. Each of the portions that respectively defines the bore has a bottom portion forming a valve seat.
- the valve seat includes a discharge port.
- the bores form chambers that are completely independent from one another.
- a rear housing is coupled to a rear end of the cylinder block.
- a suction chamber is formed in a central portion of the rear housing and opens toward a rear end of the rear housing.
- a discharge chamber is formed at the radially outer side of the suction chamber.
- a discharge valve and a retainer are arranged in the discharge port near the discharge chamber.
- the cylinder block is coupled with the rear housing to hold the discharge valve and the retainer.
- the discharge chamber has a thick outer wall that supports the partition from the rear. This suppresses deformation of the partition.
- the formation of the thick outer wall in the rear housing decreases the volume of the discharge chamber. This may increase noise by a certain amount when refrigerant is discharged.
- the thick outer wall decreases the length of the discharge valve arranged near the discharge chamber in the corresponding discharge chamber. As a result, the discharge valve becomes less flexible. This may adversely affect the moving characteristics of the discharge valve.
- One aspect of the present invention is a compressor provided with a cylinder block including a cylinder bore.
- the cylinder block includes an end.
- the end of the cylinder block includes a partition that closes one end of the cylinder bore.
- the partition includes a bottom portion forming a bottom surface of the cylinder bore.
- the bottom portion includes a discharge port, and the discharge port extends through the bottom portion and is in communication with the cylinder bore.
- a housing is coupled to the end of the cylinder block.
- the housing includes an annular outer wall, an annular inner wall located at an inner side of the outer wall, a discharge chamber formed between the outer wall and the inner wall, and a suction chamber formed at an inner side of the inner wall.
- a discharge valve is held between the cylinder block and the housing.
- the outer wall includes two partition supports that are in contact with parts of the bottom portion. The two partition supports are arranged on opposite sides of the discharge valve and extend toward the inner wall.
- FIG. 1 is a cross-sectional view entirely showing a compressor according to a first embodiment of the present invention
- FIG. 2 is a cross-sectional view taken along line A-A in FIG. 1 ;
- FIG. 3 is a cross-sectional view taken along line B-B in FIG. 1 ;
- FIG. 4 is a plan view of a discharge valve of a discharge valve shown in FIG. 1 ;
- FIG. 5 is a rear view of a front housing in the compressor shown in FIG. 1 ;
- FIG. 6 is a cross-sectional view taken along line C-C in FIG. 5 ;
- FIG. 7 is a cross-sectional view taken along line D-D in FIG. 1 ;
- FIG. 8 is a cross-sectional view taken along line E-E in FIG. 1 ;
- FIG. 9 is a front view of a rear housing in the compressor shown in FIG. 1 ;
- FIG. 10 is a front view of a rear housing in a compressor according to a second embodiment of the present invention.
- FIG. 11 is a cross-sectional view taken along line F-F in FIG. 10 ;
- FIG. 12 is a rear view of a front housing in a compressor according to a third embodiment of the present invention.
- FIG. 13 is a cross-sectional view taken along line G-G in FIG. 12 ;
- FIG. 14 is a front view of a rear housing shown in FIG. 12 .
- FIG. 1 shows a compressor 10 that is a double-headed piston swash plate compressor.
- a housing of the compressor 10 includes two coupled cylinder blocks 11 and 12 , a front housing 13 coupled to the cylinder block 11 , and a rear housing 14 coupled to the cylinder block 12 .
- Bolts 56 integrally fasten the front housing 13 , the cylinder blocks 11 and 12 , and the rear housing 14 .
- a shaft hole 11 A extends through the cylinder block 11
- a shaft hole 12 A extends through the cylinder block 12
- a rotation shaft 15 is inserted into the shaft holes 11 A and 12 A and supported to be rotatable by a sealed surface of the wall of the shaft holes 11 A and 12 A.
- the rotation shaft 15 includes a front projecting end where a lip seal type sealing device 16 is arranged between the rotation shaft 15 and an inner wall of the front housing 13 .
- the sealing device 16 is accommodated in an accommodation chamber 13 A defined between the rotation shaft 15 and the inner wall of the front housing 13 .
- a swash plate 17 which rotates integrally with the rotation shaft 15 , is fixed to the rotation shaft 15 .
- a swash plate chamber 18 is formed in the cylinder blocks 11 and 12 .
- the swash plate 17 is accommodated in the swash plate chamber 18 .
- the swash plate 17 includes an annular base 17 A.
- a thrust bearing 19 is arranged between one end of the front cylinder block 11 and the base 17 A of the swash plate 17 .
- a thrust bearing 20 is arranged between the other end of the rear cylinder block 12 and the base 17 A of the swash plate 17 .
- the thrust bearings 19 and 20 sandwich the swash plate 17 and restrict movement of the swash plate 17 in the direction of the axis L of the rotation shaft 15 . Further, the thrust bearings 19 and 20 are pressed against the open ends of the shaft holes 11 A and 12 A in the cylinder blocks 11 and 12 .
- the front cylinder block 11 includes three front cylinder bores 21 arranged around the rotation shaft 15 .
- the rear cylinder block 12 includes three rear cylinder bores 22 arranged around the rotation shaft 15 .
- the front cylinder bores 21 are paired and aligned with the rear cylinder bores 22 in the direction of the axis L.
- a double-headed piston 23 is inserted into each pair of the aligned cylinder bores 22 .
- the front end of the cylinder block 11 includes a partition 11 B that closes one end of each of the front cylinder bores 21 .
- the partition 11 B is formed integrally with the cylinder block 11 .
- the partition 11 B includes a bottom portion 11 C forming a bottom surface of each front cylinder bore 21 .
- the rear end of the cylinder block 12 includes a partition 12 B that closes one end of each of the rear cylinder bores 22 .
- the partition 12 B is formed integrally with the cylinder block 12 .
- the partition 12 B includes a bottom portion 12 C forming a bottom surface of each rear cylinder bore 22 .
- each double-headed piston 23 two shoes 24 sandwich the swash plate 17 and transmit the rotating motion of the swash plate 17 , which is rotated integrally with the rotation shaft 15 , to the double-headed piston 23 .
- This reciprocates the double-headed piston 23 in the corresponding front cylinder bore 21 and rear cylinder bore 22 .
- a front compression chamber 25 is defined in the front cylinder bore 21 between the double-headed piston 23 and the bottom portion 11 C.
- a rear compression chamber 26 is defined in the rear cylinder bore 22 between the double-headed piston 23 and the bottom portion 12 C.
- the cylinder block 11 includes three cylinder block suction chambers 27 arranged around the shaft hole 11 A. Each cylinder block suction chamber 27 is arranged between the front cylinder bores 21 that are adjacent to each other in the circumferential direction around the shaft hole 11 A. The cylinder block suction chambers 27 are arranged at equal intervals around the shaft hole 11 A. Further, the cylinder block 11 includes three cylinder block discharge chambers 29 arranged around the shaft hole 11 A. Each cylinder block discharge chamber 29 is arranged between the front cylinder bores 21 that are adjacent to each other in the circumferential direction around the shaft hole 11 A. The cylinder block discharge chambers 29 are arranged at equal intervals around the shaft hole 11 A. Further, the cylinder block discharge chambers 29 are located at the outer sides of the cylinder block suction chambers 27 in the radial direction of the cylinder block 11 .
- three discharge ports 30 extend through the bottom portion 11 C of the cylinder block 11 to communicate the front cylinder bores 21 with front discharge chambers 28 .
- a discharge valve 31 is arranged at the discharge ports 30 near the front discharge chambers 28 so as to cover the discharge ports 30 .
- the discharge valve 31 includes fixed portions 31 A, which are held between an inner wall 34 and the partition 11 B, and valve portions 31 B, which extend from the fixed portions 31 A toward an outer wall 33 .
- a gasket 32 is formed integrally with a retainer 32 A, which restricts the opening angle of the discharge valve 31 .
- the front housing 13 includes the outer wall 33 and the inner wall 34 , which is located at the inner side of the outer wall 33 .
- Each of the outer wall 33 and the inner wall 34 are annular.
- the front discharge chambers 28 are formed between the outer wall 33 and the inner wall 34
- front suction chambers 55 are formed at the inner side of the inner wall 34 .
- the front suction chambers 55 are in communication with the accommodation chamber 13 A.
- the outer wall 33 isolates the front discharge chambers 28 , which are formed at the inner side of the outer wall 33 , from the exterior and has a predetermined thickness in the radial direction.
- the outer wall 33 includes a plurality of partition supports 33 A that extend toward the inner wall 34 .
- the partition supports 33 A are in contact with parts of the bottom portions 11 C.
- the distal end of each valve portion 31 B is arranged between two of the partition supports 33 A.
- the outer wall 33 is shaped to have a predetermined thickness in the radial direction, while extending toward the inner side at portions that receive the bolts 56 .
- the outer wall 33 includes multiple pairs of the partition supports 33 A that come into contact with the bottom portion 11 C.
- the partition supports 33 A in each pair are arranged on opposite sides of the distal end of the corresponding valve portion 31 B and extend toward the inner wall 34 .
- the inner wall 34 isolates the front discharge chambers 28 , which are formed at the outer side of the inner wall 34 , from the front suction chambers 55 , which are formed at the inner side of the inner wall 34 .
- Parts of the inner wall 34 form valve supports 34 A.
- the fixed portions 31 A are held between the valve supports 34 A and the bottom portion 11 C with the valve supports 34 A partially covering parts of the bottom portion 11 C.
- ribs 35 connect the inner wall 34 and the outer wall 33 .
- the ribs 35 are opposed to the bottom portion 11 C. Further, the ribs 35 connect the valve supports 34 A of the inner wall 34 with portions of the outer wall 33 located between the two partition supports 33 A of each pair.
- the longitudinal direction of the ribs 35 conforms to the radial direction of the compressor.
- the ribs 35 each have a height T2 in the direction of axis L.
- the inner wall 34 and the outer wall 33 each have a height T1 in the direction of axis L.
- the height T2 of the ribs 35 is set to be lower than the height T1 of the inner wall 34 and the outer wall 33 .
- the cylinder block 11 and the front housing 13 are coupled to each other with the discharge valve 31 and the gasket 32 arranged in between.
- Through holes extend through the discharge valve 31 and the gasket 32 to communicate the cylinder block discharge chambers 29 , which are formed in the cylinder block 11 , with the front discharge chambers 28 , which are formed in the front housing 13 .
- through holes extend through the discharge valve 31 and the gasket 32 to communicate the front suction chambers 55 , which are formed in the front housing 13 , with the front suction chambers 55 , which are formed in the front housing 13 .
- the coupling of the cylinder block 11 and the front housing 13 with the discharge valve 31 and the gasket 32 arranged in between forms the front suction chambers 55 , which are in communication with the cylinder block suction chambers 27 and isolated from the exterior, and the front discharge chambers 28 , which are in communication with the cylinder block suction chambers 27 and isolated from the exterior.
- the cylinder block 12 includes three cylinder block suction chambers 36 arranged around the shaft hole 12 A. Each cylinder block suction chamber 36 is arranged between the rear cylinder bores 22 that are adjacent to each other in the circumferential direction around the shaft hole 12 A. The cylinder block suction chambers 36 are arranged at equal intervals around the shaft hole 12 A. Further, the cylinder block 12 includes three cylinder block discharge chambers 45 arranged around the shaft hole 12 A. Each cylinder block discharge chamber 45 is arranged between the rear cylinder bores 22 that are adjacent to each other in the circumferential direction around the shaft hole 12 A. The cylinder block discharge chambers 45 are arranged at equal intervals around the shaft hole 12 A.
- the cylinder block discharge chambers 45 are located at the outer sides of the cylinder block suction chambers 36 in the radial direction of the cylinder block 12 .
- the cylinder block suction chambers 27 are paired and aligned with the cylinder block suction chambers 36 in the direction in which the axis L extends.
- three discharge ports 39 extend through the bottom portion 12 C of the cylinder block 12 to communicate the rear cylinder bores 22 with rear discharge chambers 38 .
- a discharge valve 40 is arranged at the discharge ports 39 near the rear discharge chambers 38 so as to cover the discharge ports 39 .
- the discharge valve 40 includes fixed portions 40 A, which are held between an inner wall 43 and the partition 12 B, and valve portions 40 B, which extend from the fixed portions 40 A toward an outer wall 42 .
- a gasket 41 is formed integrally with a retainer 41 A, which restricts the opening angle of the discharge valve 40 .
- the front housing 13 includes the outer wall 42 and the inner wall 43 , which is located at the inner side of the outer wall 42 .
- Each of the outer wall 42 and the inner wall 43 are annular.
- the rear discharge chambers 38 are formed between the outer wall 42 and the inner wall 43
- rear suction chambers 57 are formed at the inner side of the inner wall 43 .
- the rear suction chambers 57 are in communication with a suction chamber 37 located at the inner side of the rear suction chambers 57 .
- the outer wall 42 isolates the rear discharge chambers 38 , which are formed at the inner side of the outer wall 42 , from the exterior and has a predetermined thickness in the radial direction.
- the outer wall 42 includes a plurality of partition supports 42 A that extend toward the inner wall 43 .
- the partition supports 42 A are in contact with parts of the bottom portions 12 C.
- the distal end of each valve portion 40 B is arranged between two of the partition supports 42 A.
- the partition supports 42 A in each pair are arranged on opposite sides of the distal end of the corresponding valve portion 40 B and extend toward the inner wall 43 .
- the inner wall 43 isolates the rear discharge chambers 38 , which are formed at the outer side of the inner wall 43 , from the rear suction chambers 57 , which are formed at the inner side of the inner wall 43 .
- Parts of the inner wall 43 form valve supports 43 A.
- the fixed portions 40 A are held between the valve supports 43 A and the bottom portion 12 C with the valve supports 43 A partially covering the bottom portion 12 C. That is, the valve supports 43 A contact the fixed portions 40 A and force the fixed portions 40 A against parts of the bottom portion 12 C.
- ribs 44 connect the inner wall 43 and the outer wall 42 .
- the ribs 44 are opposed to the bottom portion 12 C. Further, the ribs 44 connect the valve supports 43 A of the inner wall 43 with portions of the outer wall 42 located between the two partition supports 42 A of each pair.
- the longitudinal direction of the ribs 44 conforms to the radial direction of the compressor.
- the height of the ribs 44 in the direction of axis L is lower than the height of the inner wall 43 and the outer wall 42 in the direction of axis L.
- the cylinder block 12 and the rear housing 14 are coupled to each other with the discharge valve 40 and the gasket 41 arranged in between.
- Through holes extend through the discharge valve 40 and the gasket 41 to communicate the cylinder block discharge chambers 45 , which are formed in the cylinder block 12 , with the rear discharge chambers 38 , which are formed in the rear housing 14 .
- through holes extend through the discharge valve 40 and the gasket 41 to communicate the cylinder block suction chambers 36 , which are formed in the cylinder block 12 , with the rear suction chambers 57 , which are formed in the rear housing 14 .
- the coupling of the cylinder block 12 and the rear housing 14 with the discharge valve 40 and the gasket 41 arranged in between forms the rear suction chambers 57 and 37 , which are in communication with the cylinder block suction chambers 36 and isolated from the exterior, and the rear discharge chambers 38 , which are in communication with the cylinder block discharge chambers 45 and isolated from the exterior.
- a suction passage 46 extends through the cylinder blocks 11 and 12 .
- the suction passage 46 has a front opening that is in communication with one of the three cylinder block suction chambers 27 and a rear opening that is in communication with one of the three cylinder block suction chambers 36 .
- the front cylinder block 11 includes an inlet 47 .
- the inlet 47 has one end, which opens in the outer surface of the cylinder block 11 , and another end, which opens in the wall surface of the suction passage 46 .
- a pipe connects the inlet 47 to an external refrigerant circuit.
- a discharge passage 48 extends through the cylinder blocks 11 and 12 .
- the discharge passage 48 has a front opening that is in communication with one of the three cylinder block discharge chambers 29 and a rear opening that is in communication with one of the three cylinder block discharge chambers 45 .
- the front cylinder block 11 includes an outlet (not shown).
- the outlet has one end, which opens in the outer surface of the cylinder block 11 , and another end, which opens in the wall surface of the discharge passage 48 .
- a pipe connects the outlet to the external refrigerant circuit.
- the discharge passage 48 is separated from the suction passage 46 in the circumferential direction of the cylinder block.
- the cylinder block 11 includes suction chamber communication passages 50 that communicate the cylinder block suction chambers 27 and the shaft hole 11 A. Further, the cylinder block 11 includes bore communication passages 51 that communicate the shaft hole 11 A and the front cylinder bores 21 .
- the suction chamber communication passages 50 and the bore communication passages 51 are alternately arranged in the circumferential direction around the shaft hole 11 A.
- a front portion of the rotation shaft 15 includes an intake groove 52 formed in the circumferential surface.
- the intake groove 52 opens toward the sealed surface of the shaft hole 11 A and is separately communicable with the suction chamber communication passages 50 and the bore communication passages 51 .
- the rotation of the rotation shaft 15 moves the intake groove 52 and mechanically switches the suction chamber communication passages 50 and the bore communication passages 51 that are in communication with the intake groove 52 .
- the portion of the rotation shaft 15 enclosed by the sealed surface functions as a front rotary valve formed integrally with the rotation shaft 15 .
- the cylinder block 12 includes rear intake passages 53 that communicate the rear cylinder bores 22 and the shaft hole 12 A.
- a rear portion of the rotation shaft 15 includes a supply groove 54 formed in the circumferential surface.
- the supply groove 54 has one end that opens toward the suction chamber 37 in the rear housing 14 and another end that is communicable with the rear intake passages 53 .
- the rotation of the rotation shaft 15 moves the supply groove 54 and mechanically switches the rear intake passages 53 that are in communication with the supply groove 54 .
- the portion of the rotation shaft 15 enclosed by the sealed surface functions as a rear rotary valve formed integrally with the rotation shaft 15 .
- the front housing 13 includes the outer wall 33 and the inner wall 34 that define the front discharge chambers 28 and the front suction chambers 55 .
- the partition 11 B of the cylinder block 11 applies force through at least one of the discharge valve 31 and the gasket 32 to the end surface of the outer wall 33 and the end surface of the inner wall 34 .
- the partition supports 33 A extend from the outer wall 33 and are in contact with parts of the bottom portion 11 C. In the present embodiment, the partition supports 33 A are in contact with parts of the bottom portion 11 C through the gasket 32 . Thus, the area in which the front housing 13 contacts the bottom portion 11 C is increased in comparison with the prior art. This suppresses deformation of the bottom portion 11 C during compression. Further, the partition supports 33 A are arranged in pair on opposite sides of the distal ends of the valve portions 31 B. This prevents interference between the discharge valve 31 and the partition supports 33 A, while maintaining a predetermined length in the radial direction for the discharge valve 31 (length from the fixed portions 31 A to the valve portions 31 B).
- valve supports 34 A which are portions of the inner wall 34
- the valve supports 34 A are portions of the inner wall 34
- the bottom portion 11 C with the valve supports 34 A partially covering the bottom portion 11 C.
- the valve supports 34 A function to hold the fixed portions 31 A of the discharge valve 31 and function to suppress deformation of the bottom portion 11 C.
- the ribs 35 connect the inner wall 34 and the outer wall 33 and are opposed to the bottom portion 11 C. This improves the strength of the inner wall 34 and the outer wall 33 , improves the rigidity of the entire front housing 13 , and further suppresses deformation of the bottom portion 11 C during compression. Further, the height T2 of the ribs 35 in the direction of the axis L is set to be lower than the height T1 of the inner wall 34 and the outer wall 33 in the direction of the axis L. Thus, the ribs 35 do not interfere with the discharge valve 31 and the gasket 32 , and the moving characteristics of the discharge valve 31 are unaffected.
- the formation of the partition supports 33 A and the valve supports 34 A decreases the volume of the front discharge chambers 28 . However, in contrast with when entirely increasing the thickness of the outer wall 33 or the inner wall 34 , sufficient volume is ensured for the front discharge chambers 28 . This obviates the generation of noise when refrigerant is discharged.
- the refrigerant discharged to the front discharge chambers 28 flows through the cylinder block discharge chambers 29 and enters the external refrigerant circuit via the discharge passage 48 and the outlet.
- the rear housing 14 includes the outer wall 42 and the inner wall 43 that define the rear discharge chambers 38 and the rear suction chambers 57 .
- the partition 12 B of the cylinder block 12 applies force through at least one of the discharge valve 40 and the gasket 41 to the end surface of the outer wall 42 and the end surface of the inner wall 43 .
- the partition supports 42 A extend from the outer wall 42 , the inner wall 43 includes the valve supports 43 A, and the ribs 44 connect the inner wall 43 and the outer wall 42 .
- This structure is the same as the front side and obtains the same advantages as the front side.
- the outer wall 33 , the inner wall 34 , the partition supports 33 A, the valve supports 34 A, the ribs 35 , the front suction chambers 55 , and the front discharge chambers 28 at the front side correspond to the outer wall 42 , the inner wall 43 , the partition supports 42 A, the valve supports 43 A, the ribs 44 , the rear suction chambers 57 , and the rear discharge chambers 38 at the rear side.
- the refrigerant discharged to the rear discharge chambers 38 flows through the cylinder block discharge chambers 45 and enters the external refrigerant circuit via the discharge passage 48 and the outlet.
- the compressor 10 of the first embodiment has the advantages described below.
- the partition supports 33 A extend from the outer wall 33 of the front housing 13 , and the partition supports 33 A contact parts of the bottom portion 11 C. This increases the area in which the front housing 13 contacts the bottom portion 11 C and allows for deformation of the bottom portion 11 C to be suppressed during compression. Further, the partition supports 33 A are arranged in pairs so that the partition supports 33 A of each pair are arranged on opposite sides of the distal end of the corresponding valve portion 31 B. This prevents interference between the discharge valve 31 and the partition supports 33 A, maintains the length of the discharge valve 31 (length from fixed portion 31 A to valve portion 31 B) at a predetermined length, and allows for deterioration of the moving characteristics of the discharge valve 31 to be obviated.
- valve supports 34 A are formed by portions of the inner wall 34 in the front housing 13 , and the fixed portions 31 A are held between the valve supports 34 A and the bottom portion 11 C with the valve supports 34 A partially covering parts of the bottom portion 11 C. This increases the area in which the front housing 13 contacts the bottom portion 11 C and allows for deformation of the bottom portion 11 C to be further suppressed during compression. Further, the valve supports 34 A function to hold the fixed portions 31 A of the discharge valve 31 and function to suppress deformation of the bottom portion 11 C. This simplifies the structure.
- the ribs 35 connect the inner wall 34 and the outer wall 33 in the front housing 13 , and the ribs 35 are opposed to the bottom portion 11 C. This improves the rigidity of the inner wall 34 and the outer wall 33 , and allows for deformation of the bottom portion 11 C to be further suppressed during compression. Further, the height T2 of the ribs 35 in the direction of the axis L is set to be lower than the height T1 of the inner wall 34 and the outer wall 33 in the direction of the axis L. Thus, the ribs 35 , the discharge valve 31 , and the gasket 32 do not interfere with one another, and the moving characteristics of the discharge valve 31 are unaffected.
- the partition supports 42 A extend from the outer wall 42 of the rear housing 14 , and the partition supports 42 A contact parts of the bottom portion 12 C. As a result, the area in which the rear housing 14 contacts the bottom portion 12 C is increased, and deformation of the bottom portion 12 C is suppressed during compression. Further, the partition supports 42 A are arranged in pairs so that the partition supports 42 A of each pair are arranged on opposite sides of the distal end of the corresponding valve portion 40 B. This prevents interference between the discharge valve 40 and the partition supports 42 A, maintains the length of the discharge valve 40 (length from fixed portion 40 A to valve portion 40 B) at a predetermined length, and allows for deterioration of the moving characteristics of the discharge valve 40 to be obviated.
- the inner wall 43 of the rear housing 14 includes the valve supports 43 A, and the fixed portions 40 A are held between the valve supports 43 A and the bottom portion 12 C with the valve supports 43 A partially covering parts of the bottom portion 12 C. This increases the area in which the rear housing 14 contacts the bottom portion 12 C and allows for deformation of the bottom portion 12 C to be further suppressed during compression. Further, the valve supports 43 A function to hold the fixed portions 40 A of the discharge valve 40 and function to suppress deformation of the bottom portion 12 C. This simplifies the structure.
- the ribs 44 connect the inner wall 43 and the outer wall 42 in the rear housing 14 , and the ribs 44 are opposed to the bottom portion 12 C.
- the ribs 44 improve the rigidity of the inner wall 43 and the outer wall 42 , and allows for deformation of the bottom portion 12 C to be further suppressed during compression.
- the height of the ribs 44 in the direction of the axis L is set to be lower than the height of the inner wall 43 and the outer wall 42 in the direction of the axis L.
- FIGS. 10 and 11 A second embodiment of a compressor will now be described with reference to FIGS. 10 and 11 .
- the shape of the rear housing 14 is changed from the first embodiment.
- the structure of the second embodiment is the same as the first embodiment.
- Like or same reference numerals are given to those components that are the same as the corresponding components of the first embodiment. Such components will not be described in detail.
- a rear housing 61 includes cylindrical projections 62 , which are arranged on opposite sides of each rib 44 connecting the outer wall 42 and the inner wall 43 .
- the projections 62 are arranged at positions opposing the bottom portion 12 C, and the ribs 44 are arranged where interference is avoided with the partition supports 42 A and the valve supports 43 A.
- the height of each projection 62 in the direction of the axis L is the same as the height of the inner wall 43 and the outer wall 42 in the direction of the axis L.
- Each projection 62 is arranged to contact part of the bottom portion 12 C. Further, the projections 62 are arranged where interference is avoided with the discharge valve 40 and the gasket 41 . In FIG. 10 , the projections 62 are arranged at six locations.
- the projections 62 further increase the area in which the rear housing 61 contacts the bottom portion 12 C. This further suppresses deformation of the bottom portion 12 C during compression. Further, the projections 62 are arranged so that there is no interference with the discharge valve 40 . Thus, the moving characteristics of the discharge valve 40 are unaffected.
- the present embodiment also obtains advantages (1) to (8) of the first embodiment.
- a third embodiment of a compressor will now be described with reference to FIGS. 12 to 14 .
- the shapes of the front housing 13 and the rear housing 14 are changed from the first embodiment.
- the structure of the second embodiment is the same as the first embodiment.
- Like or same reference numerals are given to those components that are the same as the corresponding components of the first embodiment. Such components will not be described in detail.
- two ribs 72 connect each pair of partition supports 33 A of the outer wall 33 to the corresponding valve support 34 A of the inner wall 34 .
- the ribs 72 oppose the bottom portion 11 C.
- Each partition support 33 A is located toward the corresponding valve support 34 A as viewed from a bolt hole 75 .
- the bolt hole 75 is located along the extension of one of the ribs 72 .
- Each pair of ribs 72 extends from the corresponding pair of partition supports 33 A and is connected to the corresponding valve support 34 A. The ends of the two ribs 72 in each pair are located near each other in the proximity of the corresponding valve support 34 A. Further, as shown in FIG.
- the height T2 of the ribs 72 in the direction of the axis L is set to be lower than the height T1 of the inner wall 34 and the outer wall 33 in the direction of the axis L.
- FIG. 12 shows three pairs of ribs 72 or a total of six ribs 72 .
- two ribs 74 connect each pair of partition supports 42 A of the outer wall 42 to the corresponding valve support 43 A of the inner wall 43 .
- the ribs 74 oppose the bottom portion 12 C.
- Each partition support 42 A is located toward the corresponding valve support 43 A as viewed from a bolt hole 76 .
- the bolt hole 76 is located along the extension of one of the ribs 74 .
- Each pair of ribs 74 extends from the corresponding pair of partition supports 42 A and is connected to the corresponding valve support 43 A. The ends of the two ribs 74 in each pair are located near each other in the proximity of the corresponding valve support 43 A.
- the height of the ribs 74 in the direction of the axis L is set to be lower than the height of the inner wall 43 and the outer wall 42 in the direction of the axis L.
- the ribs 74 do not contact the discharge valve 40 and the gasket 41 .
- FIG. 14 shows three pairs of ribs 72 or a total of six ribs 72 .
- each pair of the partition supports 33 A is connected to the corresponding valve support 34 A by a pair of the ribs 72 .
- This improves the rigidity of the partition supports 33 A and the valve supports 34 A, and allows for deformation of the bottom portion 11 C to be further suppressed during compression.
- the bolt holes 75 are located along the extensions of the ribs 72 . This allows for further improvement in the rigidity of the valve supports 34 A.
- the height T2 of the ribs 72 in the direction of the axis L is set to be lower than the height T1 of the inner wall 34 and the outer wall 33 in the direction of the axis L.
- each pair of the partition supports 42 A is connected to the corresponding valve support 43 A by a pair of the ribs 74 .
- This improves the rigidity of the partition supports 42 A and the valve supports 43 A, and allows for deformation of the bottom portion 12 C to be further suppressed during compression.
- the bolt holes 76 are located along the extensions of the ribs 74 . This allows for further improvement in the rigidity of the valve supports 43 A.
- the height of the ribs 74 in the direction of the axis L is set to be lower than the height of the inner wall 43 and the outer wall 42 in the direction of the axis L.
- the ribs 74 , the discharge valve 40 , and the gasket 41 do not interfere with one another, and the moving characteristics of the discharge valve 40 are unaffected.
- the present embodiment also obtains advantages (1), (2), (4) to (6), and (8) of the first embodiment.
- the front housing and the rear housing basically have the same structure in which the partition supports extend from the outer wall, and the valve supports are formed by portions of the inner wall.
- the front and rear housings do not have to have the same structure.
- the above structure may be provided for at least only the rear housing.
- the present invention is applied to a double-headed piston swash plate compressor.
- the present invention may be applied to a single-headed piston variable displacement swash plate compressor.
- discharge and suction mechanisms may be formed by a discharge port and suction port, which are arranged in the partition of the cylinder block, and a reed discharge valve and reed suction valve.
- the present invention is applied to a compressor having three cylinders on one side and a total of six cylinders on the two sides.
- the present invention may be applied to a compressor having five cylinders on one side and a total of ten cylinders on the two sides.
- the gasket 32 (gasket 41 ) is held between the cylinder block 11 (cylinder block 12 ) and the front housing (rear housing). Instead, as long as the hermetic seal may be ensured, the gasket 32 (gasket 41 ) may be omitted. In this manner, a gasket is irrelevant to the advantages of the present invention.
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- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
A compressor is provided with a cylinder block including a cylinder bore, a housing coupled to the end of the cylinder block, and a discharge valve held between the cylinder block and the housing. An end of the cylinder block includes a partition that closes one end of the cylinder bore. The partition includes a bottom portion forming a bottom surface of the cylinder bore. The housing includes an outer wall and an inner wall. The outer wall includes two partition supports that are in contact with parts of the bottom portion. The two partition supports are arranged on opposite sides of the discharge valve and extend toward the inner wall.
Description
- The present invention relates to a compressor, and more particularly to a compressor including a cylinder block and a housing.
- Japanese Laid-Open Patent Publication No. 8-121330 describes a reciprocating compressor including single-headed pistons. The compressor includes a cylinder block having six bores. Each of the portions that respectively defines the bore has a bottom portion forming a valve seat. The valve seat includes a discharge port. The bores form chambers that are completely independent from one another. A rear housing is coupled to a rear end of the cylinder block. A suction chamber is formed in a central portion of the rear housing and opens toward a rear end of the rear housing. A discharge chamber is formed at the radially outer side of the suction chamber. A discharge valve and a retainer are arranged in the discharge port near the discharge chamber. The cylinder block is coupled with the rear housing to hold the discharge valve and the retainer.
- When a piston compresses refrigerant in a corresponding one of the bores, the pressure of the bore becomes high and deforms the valve seat (also referred to as the partition). As a result, stress may concentrate at edges in the bore and damage the partition. In the compressor of the above publication, the discharge chamber has a thick outer wall that supports the partition from the rear. This suppresses deformation of the partition. However, the formation of the thick outer wall in the rear housing decreases the volume of the discharge chamber. This may increase noise by a certain amount when refrigerant is discharged. Further, the thick outer wall decreases the length of the discharge valve arranged near the discharge chamber in the corresponding discharge chamber. As a result, the discharge valve becomes less flexible. This may adversely affect the moving characteristics of the discharge valve.
- It is an object of the present invention to provide a compressor that suppresses deformation of the partition without adversely affecting the moving characteristics of the discharge valve.
- One aspect of the present invention is a compressor provided with a cylinder block including a cylinder bore. The cylinder block includes an end. The end of the cylinder block includes a partition that closes one end of the cylinder bore. The partition includes a bottom portion forming a bottom surface of the cylinder bore. The bottom portion includes a discharge port, and the discharge port extends through the bottom portion and is in communication with the cylinder bore. A housing is coupled to the end of the cylinder block. The housing includes an annular outer wall, an annular inner wall located at an inner side of the outer wall, a discharge chamber formed between the outer wall and the inner wall, and a suction chamber formed at an inner side of the inner wall. A discharge valve is held between the cylinder block and the housing. The outer wall includes two partition supports that are in contact with parts of the bottom portion. The two partition supports are arranged on opposite sides of the discharge valve and extend toward the inner wall.
- Other aspects and advantages of the present invention will become apparent from the following description, taken in conjunction with the accompanying drawings, illustrating by way of example the principles of the invention.
- The invention, together with objects and advantages thereof, may best be understood by reference to the following description of the presently preferred embodiments together with the accompanying drawings in which:
-
FIG. 1 is a cross-sectional view entirely showing a compressor according to a first embodiment of the present invention; -
FIG. 2 is a cross-sectional view taken along line A-A inFIG. 1 ; -
FIG. 3 is a cross-sectional view taken along line B-B inFIG. 1 ; -
FIG. 4 is a plan view of a discharge valve of a discharge valve shown inFIG. 1 ; -
FIG. 5 is a rear view of a front housing in the compressor shown inFIG. 1 ; -
FIG. 6 is a cross-sectional view taken along line C-C inFIG. 5 ; -
FIG. 7 is a cross-sectional view taken along line D-D inFIG. 1 ; -
FIG. 8 is a cross-sectional view taken along line E-E inFIG. 1 ; -
FIG. 9 is a front view of a rear housing in the compressor shown inFIG. 1 ; -
FIG. 10 is a front view of a rear housing in a compressor according to a second embodiment of the present invention; -
FIG. 11 is a cross-sectional view taken along line F-F inFIG. 10 ; -
FIG. 12 is a rear view of a front housing in a compressor according to a third embodiment of the present invention; -
FIG. 13 is a cross-sectional view taken along line G-G inFIG. 12 ; and -
FIG. 14 is a front view of a rear housing shown inFIG. 12 . - A first embodiment of a compressor will now be described with reference to
FIGS. 1 to 9 .FIG. 1 shows acompressor 10 that is a double-headed piston swash plate compressor. In the present embodiment, a housing of thecompressor 10 includes two coupledcylinder blocks front housing 13 coupled to thecylinder block 11, and arear housing 14 coupled to thecylinder block 12.Bolts 56 integrally fasten thefront housing 13, the cylinder blocks 11 and 12, and therear housing 14. - A
shaft hole 11A extends through thecylinder block 11, and ashaft hole 12A extends through thecylinder block 12. Arotation shaft 15 is inserted into theshaft holes shaft holes rotation shaft 15 includes a front projecting end where a lip sealtype sealing device 16 is arranged between therotation shaft 15 and an inner wall of thefront housing 13. Thesealing device 16 is accommodated in anaccommodation chamber 13A defined between therotation shaft 15 and the inner wall of thefront housing 13. - A
swash plate 17, which rotates integrally with therotation shaft 15, is fixed to therotation shaft 15. Aswash plate chamber 18 is formed in thecylinder blocks swash plate 17 is accommodated in theswash plate chamber 18. Theswash plate 17 includes anannular base 17A. A thrust bearing 19 is arranged between one end of thefront cylinder block 11 and thebase 17A of theswash plate 17. A thrust bearing 20 is arranged between the other end of therear cylinder block 12 and thebase 17A of theswash plate 17. Thethrust bearings swash plate 17 and restrict movement of theswash plate 17 in the direction of the axis L of therotation shaft 15. Further, thethrust bearings - Referring to
FIG. 2 , thefront cylinder block 11 includes three front cylinder bores 21 arranged around therotation shaft 15. Further, referring toFIG. 7 , in the same manner as thefront cylinder block 11, therear cylinder block 12 includes three rear cylinder bores 22 arranged around therotation shaft 15. The front cylinder bores 21 are paired and aligned with the rear cylinder bores 22 in the direction of the axis L. A double-headedpiston 23 is inserted into each pair of the aligned cylinder bores 22. The front end of thecylinder block 11 includes apartition 11B that closes one end of each of the front cylinder bores 21. Thepartition 11B is formed integrally with thecylinder block 11. Thepartition 11B includes a bottom portion 11C forming a bottom surface of each front cylinder bore 21. The rear end of thecylinder block 12 includes apartition 12B that closes one end of each of the rear cylinder bores 22. Thepartition 12B is formed integrally with thecylinder block 12. Thepartition 12B includes abottom portion 12C forming a bottom surface of each rear cylinder bore 22. - In each double-headed
piston 23, twoshoes 24 sandwich theswash plate 17 and transmit the rotating motion of theswash plate 17, which is rotated integrally with therotation shaft 15, to the double-headedpiston 23. This reciprocates the double-headedpiston 23 in the corresponding front cylinder bore 21 and rear cylinder bore 22. Afront compression chamber 25 is defined in the front cylinder bore 21 between the double-headedpiston 23 and the bottom portion 11C. Arear compression chamber 26 is defined in the rear cylinder bore 22 between the double-headedpiston 23 and thebottom portion 12C. - Referring to
FIG. 2 , thecylinder block 11 includes three cylinderblock suction chambers 27 arranged around theshaft hole 11A. Each cylinderblock suction chamber 27 is arranged between the front cylinder bores 21 that are adjacent to each other in the circumferential direction around theshaft hole 11A. The cylinderblock suction chambers 27 are arranged at equal intervals around theshaft hole 11A. Further, thecylinder block 11 includes three cylinderblock discharge chambers 29 arranged around theshaft hole 11A. Each cylinderblock discharge chamber 29 is arranged between the front cylinder bores 21 that are adjacent to each other in the circumferential direction around theshaft hole 11A. The cylinderblock discharge chambers 29 are arranged at equal intervals around theshaft hole 11A. Further, the cylinderblock discharge chambers 29 are located at the outer sides of the cylinderblock suction chambers 27 in the radial direction of thecylinder block 11. - Referring to
FIGS. 1 and 3 , threedischarge ports 30 extend through the bottom portion 11C of thecylinder block 11 to communicate the front cylinder bores 21 withfront discharge chambers 28. Adischarge valve 31 is arranged at thedischarge ports 30 near thefront discharge chambers 28 so as to cover thedischarge ports 30. As shown inFIG. 4 , thedischarge valve 31 includes fixedportions 31A, which are held between aninner wall 34 and thepartition 11B, andvalve portions 31B, which extend from the fixedportions 31A toward anouter wall 33. Agasket 32 is formed integrally with aretainer 32A, which restricts the opening angle of thedischarge valve 31. - Referring to
FIGS. 3 and 5 , thefront housing 13 includes theouter wall 33 and theinner wall 34, which is located at the inner side of theouter wall 33. Each of theouter wall 33 and theinner wall 34 are annular. Thefront discharge chambers 28 are formed between theouter wall 33 and theinner wall 34, andfront suction chambers 55 are formed at the inner side of theinner wall 34. Thefront suction chambers 55 are in communication with theaccommodation chamber 13A. - The
outer wall 33 isolates thefront discharge chambers 28, which are formed at the inner side of theouter wall 33, from the exterior and has a predetermined thickness in the radial direction. Theouter wall 33 includes a plurality of partition supports 33A that extend toward theinner wall 34. The partition supports 33A are in contact with parts of the bottom portions 11C. The distal end of eachvalve portion 31B is arranged between two of the partition supports 33A. As shown by the broken lines inFIG. 5 , in the prior art, to decrease weight, theouter wall 33 is shaped to have a predetermined thickness in the radial direction, while extending toward the inner side at portions that receive thebolts 56. In the present embodiment, however, to increase the strength of the bottom portion 11C, theouter wall 33 includes multiple pairs of the partition supports 33A that come into contact with the bottom portion 11C. The partition supports 33A in each pair are arranged on opposite sides of the distal end of thecorresponding valve portion 31B and extend toward theinner wall 34. - The
inner wall 34 isolates thefront discharge chambers 28, which are formed at the outer side of theinner wall 34, from thefront suction chambers 55, which are formed at the inner side of theinner wall 34. Parts of theinner wall 34 form valve supports 34A. The fixedportions 31A are held between the valve supports 34A and the bottom portion 11C with the valve supports 34A partially covering parts of the bottom portion 11C. - As shown in
FIGS. 5 and 6 ,ribs 35 connect theinner wall 34 and theouter wall 33. Theribs 35 are opposed to the bottom portion 11C. Further, theribs 35 connect the valve supports 34A of theinner wall 34 with portions of theouter wall 33 located between the two partition supports 33A of each pair. The longitudinal direction of theribs 35 conforms to the radial direction of the compressor. Theribs 35 each have a height T2 in the direction of axis L. Theinner wall 34 and theouter wall 33 each have a height T1 in the direction of axis L. The height T2 of theribs 35 is set to be lower than the height T1 of theinner wall 34 and theouter wall 33. Thus, when thedischarge valve 31 and thegasket 32 are held between thecylinder block 11 and thefront housing 13, theribs 35 do not contact thedischarge valves 31 and thegasket 32. - As shown in
FIGS. 1 and 3 , thecylinder block 11 and thefront housing 13 are coupled to each other with thedischarge valve 31 and thegasket 32 arranged in between. Through holes extend through thedischarge valve 31 and thegasket 32 to communicate the cylinderblock discharge chambers 29, which are formed in thecylinder block 11, with thefront discharge chambers 28, which are formed in thefront housing 13. Further, through holes extend through thedischarge valve 31 and thegasket 32 to communicate thefront suction chambers 55, which are formed in thefront housing 13, with thefront suction chambers 55, which are formed in thefront housing 13. In thefront housing 13, the coupling of thecylinder block 11 and thefront housing 13 with thedischarge valve 31 and thegasket 32 arranged in between forms thefront suction chambers 55, which are in communication with the cylinderblock suction chambers 27 and isolated from the exterior, and thefront discharge chambers 28, which are in communication with the cylinderblock suction chambers 27 and isolated from the exterior. - The rear structure of the
compressor 10 will now be described. Referring toFIG. 7 , thecylinder block 12 includes three cylinderblock suction chambers 36 arranged around theshaft hole 12A. Each cylinderblock suction chamber 36 is arranged between the rear cylinder bores 22 that are adjacent to each other in the circumferential direction around theshaft hole 12A. The cylinderblock suction chambers 36 are arranged at equal intervals around theshaft hole 12A. Further, thecylinder block 12 includes three cylinderblock discharge chambers 45 arranged around theshaft hole 12A. Each cylinderblock discharge chamber 45 is arranged between the rear cylinder bores 22 that are adjacent to each other in the circumferential direction around theshaft hole 12A. The cylinderblock discharge chambers 45 are arranged at equal intervals around theshaft hole 12A. Further, the cylinderblock discharge chambers 45 are located at the outer sides of the cylinderblock suction chambers 36 in the radial direction of thecylinder block 12. The cylinderblock suction chambers 27 are paired and aligned with the cylinderblock suction chambers 36 in the direction in which the axis L extends. - Referring to
FIGS. 1 and 8 , threedischarge ports 39 extend through thebottom portion 12C of thecylinder block 12 to communicate the rear cylinder bores 22 withrear discharge chambers 38. Adischarge valve 40 is arranged at thedischarge ports 39 near therear discharge chambers 38 so as to cover thedischarge ports 39. Thedischarge valve 40 includes fixedportions 40A, which are held between aninner wall 43 and thepartition 12B, andvalve portions 40B, which extend from the fixedportions 40A toward anouter wall 42. Agasket 41 is formed integrally with aretainer 41A, which restricts the opening angle of thedischarge valve 40. - Referring to
FIGS. 8 and 9 , thefront housing 13 includes theouter wall 42 and theinner wall 43, which is located at the inner side of theouter wall 42. Each of theouter wall 42 and theinner wall 43 are annular. Therear discharge chambers 38 are formed between theouter wall 42 and theinner wall 43, andrear suction chambers 57 are formed at the inner side of theinner wall 43. Therear suction chambers 57 are in communication with asuction chamber 37 located at the inner side of therear suction chambers 57. - The
outer wall 42 isolates therear discharge chambers 38, which are formed at the inner side of theouter wall 42, from the exterior and has a predetermined thickness in the radial direction. In the same manner as the front side, theouter wall 42 includes a plurality of partition supports 42A that extend toward theinner wall 43. The partition supports 42A are in contact with parts of thebottom portions 12C. The distal end of eachvalve portion 40B is arranged between two of the partition supports 42A. The partition supports 42A in each pair are arranged on opposite sides of the distal end of thecorresponding valve portion 40B and extend toward theinner wall 43. - The
inner wall 43 isolates therear discharge chambers 38, which are formed at the outer side of theinner wall 43, from therear suction chambers 57, which are formed at the inner side of theinner wall 43. Parts of theinner wall 43 form valve supports 43A. The fixedportions 40A are held between the valve supports 43A and thebottom portion 12C with the valve supports 43A partially covering thebottom portion 12C. That is, the valve supports 43A contact thefixed portions 40A and force the fixedportions 40A against parts of thebottom portion 12C. - As shown in
FIG. 9 ,ribs 44 connect theinner wall 43 and theouter wall 42. Theribs 44 are opposed to thebottom portion 12C. Further, theribs 44 connect the valve supports 43A of theinner wall 43 with portions of theouter wall 42 located between the two partition supports 42A of each pair. The longitudinal direction of theribs 44 conforms to the radial direction of the compressor. The height of theribs 44 in the direction of axis L is lower than the height of theinner wall 43 and theouter wall 42 in the direction of axis L. Thus, when thedischarge valve 40 and thegasket 41 are held between thecylinder block 12 and therear housing 14, theribs 44 do not contact thedischarge valves 40 and thegasket 41. - As shown in
FIG. 1 , thecylinder block 12 and therear housing 14 are coupled to each other with thedischarge valve 40 and thegasket 41 arranged in between. Through holes extend through thedischarge valve 40 and thegasket 41 to communicate the cylinderblock discharge chambers 45, which are formed in thecylinder block 12, with therear discharge chambers 38, which are formed in therear housing 14. Further, through holes extend through thedischarge valve 40 and thegasket 41 to communicate the cylinderblock suction chambers 36, which are formed in thecylinder block 12, with therear suction chambers 57, which are formed in therear housing 14. In therear housing 14, the coupling of thecylinder block 12 and therear housing 14 with thedischarge valve 40 and thegasket 41 arranged in between forms therear suction chambers block suction chambers 36 and isolated from the exterior, and therear discharge chambers 38, which are in communication with the cylinderblock discharge chambers 45 and isolated from the exterior. - As shown in
FIG. 1 , asuction passage 46 extends through the cylinder blocks 11 and 12. Thesuction passage 46 has a front opening that is in communication with one of the three cylinderblock suction chambers 27 and a rear opening that is in communication with one of the three cylinderblock suction chambers 36. Further, thefront cylinder block 11 includes aninlet 47. Theinlet 47 has one end, which opens in the outer surface of thecylinder block 11, and another end, which opens in the wall surface of thesuction passage 46. A pipe connects theinlet 47 to an external refrigerant circuit. - A discharge passage 48 (refer to
FIG. 2 ) extends through the cylinder blocks 11 and 12. Thedischarge passage 48 has a front opening that is in communication with one of the three cylinderblock discharge chambers 29 and a rear opening that is in communication with one of the three cylinderblock discharge chambers 45. Further, thefront cylinder block 11 includes an outlet (not shown). The outlet has one end, which opens in the outer surface of thecylinder block 11, and another end, which opens in the wall surface of thedischarge passage 48. A pipe connects the outlet to the external refrigerant circuit. As shown inFIG. 2 , thedischarge passage 48 is separated from thesuction passage 46 in the circumferential direction of the cylinder block. - The front suction structure will now be described. As shown in
FIG. 2 , thecylinder block 11 includes suctionchamber communication passages 50 that communicate the cylinderblock suction chambers 27 and theshaft hole 11A. Further, thecylinder block 11 includesbore communication passages 51 that communicate theshaft hole 11A and the front cylinder bores 21. The suctionchamber communication passages 50 and thebore communication passages 51 are alternately arranged in the circumferential direction around theshaft hole 11A. - As shown in
FIGS. 1 and 2 , a front portion of therotation shaft 15 includes anintake groove 52 formed in the circumferential surface. Theintake groove 52 opens toward the sealed surface of theshaft hole 11A and is separately communicable with the suctionchamber communication passages 50 and thebore communication passages 51. The rotation of therotation shaft 15 moves theintake groove 52 and mechanically switches the suctionchamber communication passages 50 and thebore communication passages 51 that are in communication with theintake groove 52. In this manner, the portion of therotation shaft 15 enclosed by the sealed surface functions as a front rotary valve formed integrally with therotation shaft 15. - The rear suction structure will now be described. As shown in
FIGS. 1 and 7 , thecylinder block 12 includesrear intake passages 53 that communicate the rear cylinder bores 22 and theshaft hole 12A. Further, a rear portion of therotation shaft 15 includes asupply groove 54 formed in the circumferential surface. Thesupply groove 54 has one end that opens toward thesuction chamber 37 in therear housing 14 and another end that is communicable with therear intake passages 53. The rotation of therotation shaft 15 moves thesupply groove 54 and mechanically switches therear intake passages 53 that are in communication with thesupply groove 54. In this manner, the portion of therotation shaft 15 enclosed by the sealed surface functions as a rear rotary valve formed integrally with therotation shaft 15. - The operation of the
compressor 10 will now be described. Refrigerant is drawn through theinlet 47 into thesuction passage 46 and supplied to each of the cylinderblock suction chambers FIG. 2 , when a front cylinder bore 21 enters a suction stroke, theintake groove 52 of the front rotary valve communicates the correspondingbore communication passage 51 with an adjacent one of the suctionchamber communication passage 50. This draws refrigerant into the front cylinder bore 21 from the corresponding cylinderblock suction chamber 27 through the front rotary valve. - Further rotation of the
rotation shaft 15 moves theintake groove 52 and separates thebore communication passage 51 from the suctionchamber communication passage 50. This closes the front cylinder bore 21, and the front cylinder bore 21 shifts to the compression stroke and the discharge stroke. More specifically, the refrigerant drawn into the correspondingfront compression chamber 25 is compressed to a high pressure as the corresponding double-headedpiston 23 moves toward the front. Then, the refrigerant forcibly opens thedischarge valve 31 from thedischarge port 30 and is discharged into the correspondingfront discharge chamber 28. Here, the pressure of the refrigerant discharged from thedischarge port 30 moves thevalve portion 31B of thedischarge valve 31 to a position where thevalve portion 31B contacts theretainer 32A of thegasket 32 to open thedischarge valve 31. - In the compression stroke, the pressure of the refrigerant in the
front compression chamber 25 is high. Thus, an external force resulting from the internal pressure pushing the bottom portion 11C toward the front acts on and deforms the bottom portion 11C. When the bottom portion 11C is deformed, stress is concentrated at an edge R, which is where the bottom portion 11C and the front cylinder bore 21 are connected. Thefront housing 13 includes theouter wall 33 and theinner wall 34 that define thefront discharge chambers 28 and thefront suction chambers 55. Thepartition 11B of thecylinder block 11 applies force through at least one of thedischarge valve 31 and thegasket 32 to the end surface of theouter wall 33 and the end surface of theinner wall 34. - The partition supports 33A extend from the
outer wall 33 and are in contact with parts of the bottom portion 11C. In the present embodiment, the partition supports 33A are in contact with parts of the bottom portion 11C through thegasket 32. Thus, the area in which thefront housing 13 contacts the bottom portion 11C is increased in comparison with the prior art. This suppresses deformation of the bottom portion 11C during compression. Further, the partition supports 33A are arranged in pair on opposite sides of the distal ends of thevalve portions 31B. This prevents interference between thedischarge valve 31 and the partition supports 33A, while maintaining a predetermined length in the radial direction for the discharge valve 31 (length from the fixedportions 31A to thevalve portions 31B). - Further, the fixed
portions 31A are held between the valve supports 34A, which are portions of theinner wall 34, and the bottom portion 11C with the valve supports 34A partially covering the bottom portion 11C. Thus, the area in which thefront housing 13 contacts the bottom portion 11C is increased in comparison with the prior art. This further suppresses deformation of the bottom portion 11C during compression. The valve supports 34A function to hold the fixedportions 31A of thedischarge valve 31 and function to suppress deformation of the bottom portion 11C. - The
ribs 35 connect theinner wall 34 and theouter wall 33 and are opposed to the bottom portion 11C. This improves the strength of theinner wall 34 and theouter wall 33, improves the rigidity of the entirefront housing 13, and further suppresses deformation of the bottom portion 11C during compression. Further, the height T2 of theribs 35 in the direction of the axis L is set to be lower than the height T1 of theinner wall 34 and theouter wall 33 in the direction of the axis L. Thus, theribs 35 do not interfere with thedischarge valve 31 and thegasket 32, and the moving characteristics of thedischarge valve 31 are unaffected. - The formation of the partition supports 33A and the valve supports 34A decreases the volume of the
front discharge chambers 28. However, in contrast with when entirely increasing the thickness of theouter wall 33 or theinner wall 34, sufficient volume is ensured for thefront discharge chambers 28. This obviates the generation of noise when refrigerant is discharged. The refrigerant discharged to thefront discharge chambers 28 flows through the cylinderblock discharge chambers 29 and enters the external refrigerant circuit via thedischarge passage 48 and the outlet. - At the rear side of the compressor, when refrigerant is drawn into the
suction chamber 37, if a rear cylinder bore 22 enters a suction stroke, thesupply groove 54 of the rear rotary valve, which is in communication with thesuction chamber 37, comes into communication with the correspondingrear intake passage 53. This draws refrigerant from thesuction chamber 37 through the rear rotary valve and into therear intake passage 53. The refrigerant is further drawn into the cylinder bore 22 that is in communication with therear intake passage 53. - Further rotation of the
rotation shaft 15 separates thesupply groove 54 from therear intake passage 53 and closes the rear cylinder bore 22. Then, the rear cylinder bore 22 shifts to the compression stroke and the discharge stroke. More specifically, the refrigerant drawn into the correspondingrear compression chamber 26 is compressed to a high pressure as the corresponding double-headedpiston 23 moves toward the rear. Then, the refrigerant forcibly opens thedischarge valve 40 from thedischarge port 39 and is discharged into the correspondingrear discharge chamber 38. Here, the pressure of the refrigerant discharged from thedischarge port 39 moves thevalve portion 40B of thedischarge valve 40 to a position where thevalve portion 40B contacts theretainer 41A of thegasket 41 to open thedischarge valve 40. - In the compression stroke, the pressure of the refrigerant in the
rear compression chamber 26 is high. Thus, an external force acts on and deforms thebottom portion 12C. When thebottom portion 12C is deformed, stress is concentrated at an edge R, which is where thebottom portion 12C and the rear cylinder bore 22 are connected. In the same manner as thefront housing 13, therear housing 14 includes theouter wall 42 and theinner wall 43 that define therear discharge chambers 38 and therear suction chambers 57. Thepartition 12B of thecylinder block 12 applies force through at least one of thedischarge valve 40 and thegasket 41 to the end surface of theouter wall 42 and the end surface of theinner wall 43. - The partition supports 42A extend from the
outer wall 42, theinner wall 43 includes the valve supports 43A, and theribs 44 connect theinner wall 43 and theouter wall 42. This structure is the same as the front side and obtains the same advantages as the front side. Theouter wall 33, theinner wall 34, the partition supports 33A, the valve supports 34A, theribs 35, thefront suction chambers 55, and thefront discharge chambers 28 at the front side correspond to theouter wall 42, theinner wall 43, the partition supports 42A, the valve supports 43A, theribs 44, therear suction chambers 57, and therear discharge chambers 38 at the rear side. The refrigerant discharged to therear discharge chambers 38 flows through the cylinderblock discharge chambers 45 and enters the external refrigerant circuit via thedischarge passage 48 and the outlet. - The
compressor 10 of the first embodiment has the advantages described below. - (1) The partition supports 33A extend from the
outer wall 33 of thefront housing 13, and the partition supports 33A contact parts of the bottom portion 11C. This increases the area in which thefront housing 13 contacts the bottom portion 11C and allows for deformation of the bottom portion 11C to be suppressed during compression. Further, the partition supports 33A are arranged in pairs so that the partition supports 33A of each pair are arranged on opposite sides of the distal end of thecorresponding valve portion 31B. This prevents interference between thedischarge valve 31 and the partition supports 33A, maintains the length of the discharge valve 31 (length from fixedportion 31A tovalve portion 31B) at a predetermined length, and allows for deterioration of the moving characteristics of thedischarge valve 31 to be obviated. - (2) The valve supports 34A are formed by portions of the
inner wall 34 in thefront housing 13, and the fixedportions 31A are held between the valve supports 34A and the bottom portion 11C with the valve supports 34A partially covering parts of the bottom portion 11C. This increases the area in which thefront housing 13 contacts the bottom portion 11C and allows for deformation of the bottom portion 11C to be further suppressed during compression. Further, the valve supports 34A function to hold the fixedportions 31A of thedischarge valve 31 and function to suppress deformation of the bottom portion 11C. This simplifies the structure. - (3) The
ribs 35 connect theinner wall 34 and theouter wall 33 in thefront housing 13, and theribs 35 are opposed to the bottom portion 11C. This improves the rigidity of theinner wall 34 and theouter wall 33, and allows for deformation of the bottom portion 11C to be further suppressed during compression. Further, the height T2 of theribs 35 in the direction of the axis L is set to be lower than the height T1 of theinner wall 34 and theouter wall 33 in the direction of the axis L. Thus, theribs 35, thedischarge valve 31, and thegasket 32 do not interfere with one another, and the moving characteristics of thedischarge valve 31 are unaffected. - (4) The formation of the partition supports 33A and the valve supports 34A in the
front housing 13 decreases the volume of thefront discharge chambers 28. However, in contrast with when entirely increasing the thickness of theouter wall 33 or theinner wall 34, sufficient volume is ensured for thefront discharge chambers 28. This obviates the generation of noise when refrigerant is discharged. - (5) The partition supports 42A extend from the
outer wall 42 of therear housing 14, and the partition supports 42A contact parts of thebottom portion 12C. As a result, the area in which therear housing 14 contacts thebottom portion 12C is increased, and deformation of thebottom portion 12C is suppressed during compression. Further, the partition supports 42A are arranged in pairs so that the partition supports 42A of each pair are arranged on opposite sides of the distal end of thecorresponding valve portion 40B. This prevents interference between thedischarge valve 40 and the partition supports 42A, maintains the length of the discharge valve 40 (length from fixedportion 40A tovalve portion 40B) at a predetermined length, and allows for deterioration of the moving characteristics of thedischarge valve 40 to be obviated. - (6) The
inner wall 43 of therear housing 14 includes the valve supports 43A, and the fixedportions 40A are held between the valve supports 43A and thebottom portion 12C with the valve supports 43A partially covering parts of thebottom portion 12C. This increases the area in which therear housing 14 contacts thebottom portion 12C and allows for deformation of thebottom portion 12C to be further suppressed during compression. Further, the valve supports 43A function to hold the fixedportions 40A of thedischarge valve 40 and function to suppress deformation of thebottom portion 12C. This simplifies the structure. - (7) The
ribs 44 connect theinner wall 43 and theouter wall 42 in therear housing 14, and theribs 44 are opposed to thebottom portion 12C. Theribs 44 improve the rigidity of theinner wall 43 and theouter wall 42, and allows for deformation of thebottom portion 12C to be further suppressed during compression. Further, the height of theribs 44 in the direction of the axis L is set to be lower than the height of theinner wall 43 and theouter wall 42 in the direction of the axis L. Thus, theribs 44, thedischarge valve 40, and thegasket 41 do not interfere with one another, and the moving characteristics of thedischarge valve 40 are unaffected. - (8) The formation of the partition supports 42A and the valve supports 43A in the
rear housing 14 decreases the volume of therear discharge chambers 38. However, in contrast with when entirely increasing the thickness of theouter wall 42 or theinner wall 43, sufficient volume is ensured for therear discharge chambers 38. This obviates the generation of noise when refrigerant is discharged. - A second embodiment of a compressor will now be described with reference to
FIGS. 10 and 11 . In this embodiment, the shape of therear housing 14 is changed from the first embodiment. Otherwise, the structure of the second embodiment is the same as the first embodiment. Like or same reference numerals are given to those components that are the same as the corresponding components of the first embodiment. Such components will not be described in detail. - As shown in
FIGS. 10 and 11 , in the present embodiment, arear housing 61 includescylindrical projections 62, which are arranged on opposite sides of eachrib 44 connecting theouter wall 42 and theinner wall 43. Theprojections 62 are arranged at positions opposing thebottom portion 12C, and theribs 44 are arranged where interference is avoided with the partition supports 42A and the valve supports 43A. The height of eachprojection 62 in the direction of the axis L is the same as the height of theinner wall 43 and theouter wall 42 in the direction of the axis L. Eachprojection 62 is arranged to contact part of thebottom portion 12C. Further, theprojections 62 are arranged where interference is avoided with thedischarge valve 40 and thegasket 41. InFIG. 10 , theprojections 62 are arranged at six locations. - The
projections 62 further increase the area in which therear housing 61 contacts thebottom portion 12C. This further suppresses deformation of thebottom portion 12C during compression. Further, theprojections 62 are arranged so that there is no interference with thedischarge valve 40. Thus, the moving characteristics of thedischarge valve 40 are unaffected. The present embodiment also obtains advantages (1) to (8) of the first embodiment. - A third embodiment of a compressor will now be described with reference to
FIGS. 12 to 14 . In this embodiment, the shapes of thefront housing 13 and therear housing 14 are changed from the first embodiment. Otherwise, the structure of the second embodiment is the same as the first embodiment. Like or same reference numerals are given to those components that are the same as the corresponding components of the first embodiment. Such components will not be described in detail. - As shown in
FIG. 12 , in afront housing 71 of the present embodiment, tworibs 72 connect each pair of partition supports 33A of theouter wall 33 to thecorresponding valve support 34A of theinner wall 34. Theribs 72 oppose the bottom portion 11C. Eachpartition support 33A is located toward the correspondingvalve support 34A as viewed from abolt hole 75. Thebolt hole 75 is located along the extension of one of theribs 72. Each pair ofribs 72 extends from the corresponding pair of partition supports 33A and is connected to thecorresponding valve support 34A. The ends of the tworibs 72 in each pair are located near each other in the proximity of thecorresponding valve support 34A. Further, as shown inFIG. 13 , the height T2 of theribs 72 in the direction of the axis L is set to be lower than the height T1 of theinner wall 34 and theouter wall 33 in the direction of the axis L. Thus, when thedischarge valve 31 and thegasket 32 are held between thecylinder block 11 and thefront housing 71, theribs 72 do not contact thedischarge valve 31 and thegasket 32.FIG. 12 shows three pairs ofribs 72 or a total of sixribs 72. - As shown in
FIG. 14 , in arear housing 73 of the present embodiment, tworibs 74 connect each pair of partition supports 42A of theouter wall 42 to thecorresponding valve support 43A of theinner wall 43. Theribs 74 oppose thebottom portion 12C. Eachpartition support 42A is located toward the correspondingvalve support 43A as viewed from abolt hole 76. Thebolt hole 76 is located along the extension of one of theribs 74. Each pair ofribs 74 extends from the corresponding pair of partition supports 42A and is connected to thecorresponding valve support 43A. The ends of the tworibs 74 in each pair are located near each other in the proximity of thecorresponding valve support 43A. Further, although not shown in the drawings, the height of theribs 74 in the direction of the axis L is set to be lower than the height of theinner wall 43 and theouter wall 42 in the direction of the axis L. Thus, when thedischarge valve 40 and thegasket 41 are held between thecylinder block 12 and therear housing 73, theribs 74 do not contact thedischarge valve 40 and thegasket 41.FIG. 14 shows three pairs ofribs 72 or a total of sixribs 72. - In the
front housing 71, each pair of the partition supports 33A is connected to thecorresponding valve support 34A by a pair of theribs 72. This improves the rigidity of the partition supports 33A and the valve supports 34A, and allows for deformation of the bottom portion 11C to be further suppressed during compression. Further, the bolt holes 75 are located along the extensions of theribs 72. This allows for further improvement in the rigidity of the valve supports 34A. Further, the height T2 of theribs 72 in the direction of the axis L is set to be lower than the height T1 of theinner wall 34 and theouter wall 33 in the direction of the axis L. Thus, theribs 72, thedischarge valve 31, and thegasket 32 do not interfere with one another, and the moving characteristics of thedischarge valve 31 are unaffected. - In the
rear housing 73, each pair of the partition supports 42A is connected to thecorresponding valve support 43A by a pair of theribs 74. This improves the rigidity of the partition supports 42A and the valve supports 43A, and allows for deformation of thebottom portion 12C to be further suppressed during compression. Further, the bolt holes 76 are located along the extensions of theribs 74. This allows for further improvement in the rigidity of the valve supports 43A. Further, the height of theribs 74 in the direction of the axis L is set to be lower than the height of theinner wall 43 and theouter wall 42 in the direction of the axis L. Thus, theribs 74, thedischarge valve 40, and thegasket 41 do not interfere with one another, and the moving characteristics of thedischarge valve 40 are unaffected. The present embodiment also obtains advantages (1), (2), (4) to (6), and (8) of the first embodiment. - It should be apparent to those skilled in the art that the present invention may be embodied in many other specific forms without departing from the spirit or scope of the invention. Particularly, it should be understood that the present invention may be embodied in the following forms.
- In the first to third embodiments, the front housing and the rear housing basically have the same structure in which the partition supports extend from the outer wall, and the valve supports are formed by portions of the inner wall. However, the front and rear housings do not have to have the same structure. For example, the above structure may be provided for at least only the rear housing.
- In the first to third embodiments, the present invention is applied to a double-headed piston swash plate compressor. Instead, the present invention may be applied to a single-headed piston variable displacement swash plate compressor. Further, instead of rotary valves, discharge and suction mechanisms may be formed by a discharge port and suction port, which are arranged in the partition of the cylinder block, and a reed discharge valve and reed suction valve.
- In the first to third embodiment, the present invention is applied to a compressor having three cylinders on one side and a total of six cylinders on the two sides. Instead, the present invention may be applied to a compressor having five cylinders on one side and a total of ten cylinders on the two sides.
- In the first to third embodiments, the gasket 32 (gasket 41) is held between the cylinder block 11 (cylinder block 12) and the front housing (rear housing). Instead, as long as the hermetic seal may be ensured, the gasket 32 (gasket 41) may be omitted. In this manner, a gasket is irrelevant to the advantages of the present invention.
- The present examples and embodiments are to be considered as illustrative and not restrictive, and the invention is not to be limited to the details given herein, but may be modified within the scope and equivalence of the appended claims.
Claims (6)
1. A compressor comprising:
a cylinder block including a cylinder bore, wherein the cylinder block includes an end, the end of the cylinder block includes a partition that closes one end of the cylinder bore, the partition includes a bottom portion forming a bottom surface of the cylinder bore, the bottom portion includes a discharge port, and the discharge port extends through the bottom portion and is in communication with the cylinder bore;
a housing coupled to the end of the cylinder block, wherein the housing includes an annular outer wall, an annular inner wall located at an inner side of the outer wall, a discharge chamber formed between the outer wall and the inner wall, and a suction chamber formed at an inner side of the inner wall; and
a discharge valve held between the cylinder block and the housing, wherein
the outer wall includes two partition supports that are in contact with parts of the bottom portion, and
the two partition supports are arranged on opposite sides of the discharge valve and extend toward the inner wall.
2. The compressor according to claim 1 , wherein
the discharge valve includes a fixed portion, which is held between the cylinder block and the housing, and a valve portion, which is capable of closing the discharge port;
the inner wall includes a valve support that holds the fixed portion with the partition; and
the valve support is in contact with part of the bottom portion.
3. The compressor according to claim 1 , wherein
the housing includes a rib that connects the inner wall and the outer wall,
the rib has a lower height than the inner wall and the outer wall, and
the rib opposes the bottom portion.
4. The compressor according to claim 3 , wherein
the rib is one of two ribs, and
the two ribs are respectively extended from the two partition supports toward the inner wall and connected to the inner wall.
5. The compressor according to claim 2 , wherein
the housing includes a rib that connects the inner wall and the outer wall,
the rib has a lower height than the inner wall and the outer wall, and
the rib opposes the bottom portion.
6. The compressor according to claim 5 , wherein
the rib is one of two ribs, and
the two ribs are respectively extended from the two partition supports toward the inner wall and connected to the inner wall.
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2012215190 | 2012-09-27 | ||
JP2012-215190 | 2012-09-27 | ||
JP2013-110570 | 2013-05-27 | ||
JP2013110570A JP2014080965A (en) | 2012-09-27 | 2013-05-27 | Compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
US20140086760A1 true US20140086760A1 (en) | 2014-03-27 |
Family
ID=50339030
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/031,543 Abandoned US20140086760A1 (en) | 2012-09-27 | 2013-09-19 | Compressor |
Country Status (5)
Country | Link |
---|---|
US (1) | US20140086760A1 (en) |
JP (1) | JP2014080965A (en) |
KR (1) | KR101475729B1 (en) |
CN (1) | CN103696929A (en) |
BR (1) | BR102013024665A2 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20160208787A1 (en) * | 2015-01-21 | 2016-07-21 | Kabushiki Kaisha Toyota Jidoshokki | Double- headed piston type swash plate compressor |
US10859061B2 (en) * | 2017-03-09 | 2020-12-08 | Mahle International Gmbh | Axial piston machine |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR101926923B1 (en) * | 2016-11-02 | 2018-12-07 | 현대자동차주식회사 | Air-conditioner compressor for vehicle |
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US4886424A (en) * | 1987-03-11 | 1989-12-12 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Multi-piston swash plate type compressor with damping arrangement for discharge reed valves |
US5533870A (en) * | 1992-11-13 | 1996-07-09 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Piston type compressor |
US5607287A (en) * | 1994-12-16 | 1997-03-04 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Reciprocating piston type compressor with an improved discharge valve mechanism |
US5702236A (en) * | 1994-02-23 | 1997-12-30 | Kabushiki Kaisha Toyoda Jiboshokki Seisakusho | Reciprocating piston type compressor having a discharge chamber with a plurality of pulsation attenuating subchambers |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
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JPH036873Y2 (en) * | 1986-01-17 | 1991-02-20 | ||
JPH08121330A (en) * | 1994-10-27 | 1996-05-14 | Toyota Autom Loom Works Ltd | Reciprocating type compressor |
JPH08200218A (en) * | 1995-01-31 | 1996-08-06 | Toyota Autom Loom Works Ltd | Reciprocation type compressor |
JPH109136A (en) * | 1996-06-24 | 1998-01-13 | Toyota Autom Loom Works Ltd | Compressor |
JP4810701B2 (en) * | 2001-07-24 | 2011-11-09 | 株式会社ヴァレオジャパン | Reciprocating refrigerant compressor |
JP4003673B2 (en) * | 2003-03-13 | 2007-11-07 | 株式会社豊田自動織機 | Piston compressor |
KR101104281B1 (en) * | 2005-09-02 | 2012-01-12 | 한라공조주식회사 | Compressor |
CN101769375B (en) * | 2008-12-29 | 2014-10-01 | 上海三电贝洱汽车空调有限公司 | Cylinder cover cushion |
KR20110003827A (en) * | 2009-07-06 | 2011-01-13 | 한라공조주식회사 | Compressor |
-
2013
- 2013-05-27 JP JP2013110570A patent/JP2014080965A/en not_active Withdrawn
- 2013-09-19 US US14/031,543 patent/US20140086760A1/en not_active Abandoned
- 2013-09-24 KR KR1020130113373A patent/KR101475729B1/en not_active IP Right Cessation
- 2013-09-25 BR BR102013024665A patent/BR102013024665A2/en not_active IP Right Cessation
- 2013-09-25 CN CN201310449814.9A patent/CN103696929A/en active Pending
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
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US4886424A (en) * | 1987-03-11 | 1989-12-12 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Multi-piston swash plate type compressor with damping arrangement for discharge reed valves |
US5533870A (en) * | 1992-11-13 | 1996-07-09 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Piston type compressor |
US5702236A (en) * | 1994-02-23 | 1997-12-30 | Kabushiki Kaisha Toyoda Jiboshokki Seisakusho | Reciprocating piston type compressor having a discharge chamber with a plurality of pulsation attenuating subchambers |
US5607287A (en) * | 1994-12-16 | 1997-03-04 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Reciprocating piston type compressor with an improved discharge valve mechanism |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20160208787A1 (en) * | 2015-01-21 | 2016-07-21 | Kabushiki Kaisha Toyota Jidoshokki | Double- headed piston type swash plate compressor |
US10859061B2 (en) * | 2017-03-09 | 2020-12-08 | Mahle International Gmbh | Axial piston machine |
Also Published As
Publication number | Publication date |
---|---|
KR20140041354A (en) | 2014-04-04 |
BR102013024665A2 (en) | 2016-04-26 |
JP2014080965A (en) | 2014-05-08 |
KR101475729B1 (en) | 2014-12-23 |
CN103696929A (en) | 2014-04-02 |
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Owner name: KABUSHIKI KAISHA TOYOTA JIDOSHOKKI, JAPAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:NISHIDA, KENJI;BANNO, NOBUTOSHI;KONDO, JUN;AND OTHERS;REEL/FRAME:031241/0939 Effective date: 20130917 |
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