US20140294617A1 - Piston type swash plate compressor - Google Patents
Piston type swash plate compressor Download PDFInfo
- Publication number
- US20140294617A1 US20140294617A1 US14/221,617 US201414221617A US2014294617A1 US 20140294617 A1 US20140294617 A1 US 20140294617A1 US 201414221617 A US201414221617 A US 201414221617A US 2014294617 A1 US2014294617 A1 US 2014294617A1
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- Prior art keywords
- side discharge
- head
- block
- cylinder
- chambers
- 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.)
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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
- F04B27/0804—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 rotary 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
- 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
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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
-
- 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
- F04B25/00—Multi-stage pumps
- F04B25/04—Multi-stage pumps having cylinders coaxial with, or parallel or inclined to, main shaft axis
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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
- F04B39/0027—Pulsation and noise damping means
- F04B39/0033—Pulsation and noise damping means with encapsulations
- F04B39/0038—Pulsation and noise damping means with encapsulations of inlet or outlet channels
Definitions
- the present invention relates to a piston type swash plate compressor.
- a compressor including a muffler for reducing the pulsation.
- Japanese Patent Application Publication No. 10-89251 discloses a compressor wherein a muffler space is formed in a compressor housing, a compression chamber is connected to the muffler space and a meandering member is provided in the muffler space for defining a passage for meandering discharged gas.
- the present invention which has been made in light of the above problems, is directed to providing a piston type swash plate compressor which can reduce the pulsation without being large in size.
- a piston type swash plate compressor includes a housing, a cylinder block, a cylinder head, a rotary shaft, a plurality of cylinder bores, a plurality of pistons, a swash plate, a plurality of compression chambers, a plurality of head-side discharge chambers, a plurality of block-side discharge chambers, an outlet and a discharge path.
- the cylinder block is formed in the housing.
- the cylinder head is formed in the housing and connected to an end of the cylinder block.
- the rotary shaft is rotatably supported by the cylinder block.
- a plurality of cylinder bores is arranged around the rotary shaft.
- a plurality of pistons is respectively accommodated in the cylinder bores.
- the swash plate integrally rotates with the rotary shaft and is engaged with the pistons.
- a plurality of the compression chambers is respectively defined in the cylinder bores by the pistons.
- a plurality of the head-side discharge chambers is provided in the cylinder head.
- a plurality of the block-side discharge chambers is provided in the cylinder block.
- the outlet is formed in the housing and compressed refrigerant gas is flowed outside of the housing through the outlet.
- the discharge path is formed in the housing and refrigerant gas is flowed through the discharge path from the compression chamber to the outlet to the block-side discharge chamber through the head-side discharge chamber. After refrigerant gas flowed from the compression chamber is flowed through one head-side discharge chamber which communicates with the compression chamber and one block-side discharge chamber, the refrigerant gas is flowed to another head-side discharge chamber.
- FIG. 1 is a sectional view taken along the line I-I in FIG. 3 showing a double-headed piston type swash plate compressor according to a first preferred embodiment of the present invention
- FIG. 2 is a sectional view taken along the line II-II in FIG. 3 showing the double-headed piston type swash plate compressor of FIG. 1 ;
- FIG. 3 is a sectional view taken along the line in FIG. 1 showing front head-side discharge chambers and front suction chambers of the double-headed piston type swash plate compressor of FIG. 1 ;
- FIG. 4 is a sectional view taken along the line IV-IV in FIG. 1 showing front block-side discharge chambers and the front suction chambers of the double-headed piston type swash plate compressor of FIG. 1 ;
- FIG. 5 is a sectional view taken along the line V-V in FIG. 1 showing the front head-side discharge chambers and front partition walls of the double-headed piston type swash plate compressor of FIG. 1 ;
- FIG. 6 is a sectional view showing the front head-side discharge chambers, front compression chambers and the front block-side discharge chambers expanded in a rotating direction of a rotary shaft of the double-headed piston type swash plate compressor of FIG. 1 ;
- FIG. 7 is a sectional view taken along the line VII-VII in FIG. 1 showing the rear head-side discharge chambers and rear partition walls of the double-headed piston type swash plate compressor of FIG. 1 .
- reference numeral 10 designates a double-headed piston type swash plate compressor (hereinafter simply referred to as “compressor”) and the compressor 10 includes a housing H and a pair of front and rear cylinder blocks 11 and 12 connected to each other.
- a front cylinder head 13 is disposed on the front side of the compressor 10 (the left side in FIG. 1 ) and coupled to the front end of the front cylinder block 11 through the front valve plate assembly 15 .
- the front valve plate assembly 15 includes a gasket G for sealing a space between the front cylinder block 11 and the front cylinder head 13 and a valve plate 20 a part of which forms a front discharge valve 15 B which will be describe later.
- a rear cylinder head 14 is disposed on a rear side of the compressor 10 (the right side in FIG. 1 ) and coupled to the rear end of the rear cylinder block 12 through a rear valve plate assembly 16 .
- the rear valve plate assembly 16 includes the gasket G for sealing a space between the rear cylinder block 12 and the rear cylinder head 14 and a rear valve plate 21 a part of which forms a rear discharge valve 16 B which will be described later.
- the front and the rear cylinder blocks 11 and 12 serve as a cylinder block of the present invention.
- the front and the rear cylinder heads 13 and 14 serve as a cylinder head of the present invention.
- the front and the rear valve plate assemblies 15 and 16 serve as a valve plate assembly of the present invention.
- the front and the rear discharge valves 15 B and 16 B serve as a discharge valve of the present invention.
- the front and the rear valve plates 20 and 21 serve as a valve plate of the present invention.
- the front and the rear cylinder blocks 11 and 12 include front and rear shaft holes 11 A and 12 A, respectively, and a rotary shaft 22 is inserted through the front and the rear shaft holes 11 A and 12 A so as to be rotatably supported by the inner circumferential surfaces of the front and the rear shaft holes 11 A and 12 A which form a sealing circumferential surface.
- the front and the rear valve plate assemblies 15 and 16 include front and rear insertion holes 15 D and 16 D formed at the centers thereof, respectively, and the rotary shaft 22 is inserted through the front and the rear insertion holes 15 D and 16 D.
- a shaft seal 23 of a lip seal type hermetically seals a space between the outer circumferential surface of the front end of the rotary shaft 22 extending out of the front valve plate assembly 15 and the inner circumferential surface of the front cylinder head 13 .
- the shaft seal 23 is provided in an accommodation chamber 13 C formed between the inner circumferential surface of the front cylinder head 13 and the outer circumferential surface of the rotary shaft 22 .
- the front and the rear shaft holes 11 A and 12 A serve a shaft hole of the present invention.
- the front and the rear insertion holes 15 D and 16 D serve an insertion hole of the present invention.
- a swash plate 24 which integrally rotates with the rotary shaft 22 , is firmly fixed to the rotary shaft 22 .
- the swash plate 24 is disposed in a crank chamber 25 formed between the front and the rear cylinder blocks 11 and 12 .
- a front thrust bearing 26 is interposed between the rear end surface of the front cylinder block 11 and an annular base portion 24 A of the swash plate 24 .
- a rear thrust bearing 27 is interposed between the front end surface of the rear cylinder block 12 and the base portion 24 A of the swash plate 24 .
- the front and the rear thrust bearings 26 and 27 hold the swash plate 24 and regulate the movement of the swash plate 24 along the center axis L of the rotary shaft 22 .
- the front and the rear thrust bearings 26 and 27 serve as a thrust bearing of the present invention.
- three front cylinder bores 28 are arranged around the rotary shaft 22 in the front cylinder block 11 .
- three rear cylinder bores 29 are arranged around the rotary shaft 22 in the rear cylinder block 12 .
- the paired front and rear cylinder bores 28 and 29 formed to extend along the center axis L of the rotary shaft 22 (in the longitudinal direction of the compressor 10 ).
- Double-headed pistons 30 are received in the front and the rear cylinder bores 28 and 29 , respectively.
- the front cylinder bore 28 is closed by the front valve plate assembly 15 and the double-headed piston 30 and the rear cylinder bore 29 is closed by the rear valve plate assembly 16 and the double-headed piston 30 .
- the front and the rear cylinder bores 28 and 29 serve as a cylinder bore of the present invention.
- a front compression chamber 28 A is defined in the front cylinder bore 28 by the double-headed piston 30 and the front valve plate assembly 15 and a rear compression chamber 29 A is defined in the rear cylinder bore 29 by the double-headed piston 30 and the rear valve plate assembly 16 .
- the front and the rear compression chambers 28 A and 29 A serve as a compression chamber of the present invention.
- each front suction chamber 17 is located between any two adjacent front cylinder bores 28 and each rear suction chamber 18 is located between any two adjacent rear cylinder bores 29 .
- the front and the rear suction chambers 17 and 18 are arranged at equal intervals on the outer circumference side of the front and the rear shaft holes 11 A and 12 A, respectively.
- One front suction chamber 17 has a length in the axial direction of the rotary shaft 22 and a volume larger than the length and the volume of the other front suction chamber 17 and one rear suction chamber 18 has a length in the axial direction of the rotary shaft 22 and a volume larger than the length and the volume of the other rear suction chamber 18 .
- the front and the rear suction chambers 17 and 18 serve as a suction chamber of the present invention.
- each of the three front suction chambers 17 communicates with the accommodation chamber 13 C and three front suction chambers 17 communicate with each other through the accommodation chamber 13 C.
- the three front suction chambers 17 and the accommodation chamber 13 C form one space.
- three first through third front head-side discharge chambers 33 A through 33 C are located so as to surround the rotary shaft 22 between the front cylinder head 13 and the front valve plate assembly 15 and three first through third rear head-side discharge chambers 35 A through 35 C are located so as to surround the rotary shaft 22 between the rear cylinder head 14 and the rear valve plate assembly 16 .
- Refrigerant gas flowed from the front and the rear compression chambers 28 A and 29 A is discharged to the first through the third front head-side discharge chambers 33 A through 33 C and the first through the third rear head-side discharge chambers 35 A through 35 C, respectively.
- a front space 28 B is formed around the rotary shaft 22 in the front cylinder head 13 and partitioned to the first through the third front head-side discharge chambers 33 A through 33 C.
- a rear space 29 B is formed around the rotary shaft 22 in the rear cylinder head 14 and partitioned to the first through the third rear head-side discharge chambers 35 A through 35 C.
- the size of the openings of the first through the third front head-side discharge chambers 33 A through 33 C and the first through the third rear head-side discharge chambers 35 A through 35 C at positions facing the front and the rear compression chambers 28 A and 29 A through the front and the rear valve plate assemblies 15 and 16 is the same as the circular section of the front and the rear compression chambers 28 A and 29 A (the front and the rear cylinder bores 28 and 29 ).
- the first through the third front head-side discharge chambers 33 A through 33 C and the first through the third rear head-side discharge chambers 35 A through 35 C serve as a head-side discharge chamber of the present invention.
- the front and the rear spaces 28 B and 29 B serve as a space of the present invention.
- Three front block-side discharge chambers 40 are formed in the front cylinder block 11 and three rear block-side discharge chambers 42 are formed in the rear cylinder block 12 .
- the front compression chambers 28 A, the first through the third front head-side discharge chambers 33 A through 33 C and the front block-side discharge chambers 40 communicate with one another and the rear compression chambers 29 A, the first through the third rear head-side discharge chambers 35 A through 35 C and the rear block-side discharge chambers 42 communicate with one another.
- the three front block-side discharge chambers 40 are located around the rotary shaft 22 and each front block-side discharge chamber 40 is located between any two adjacent front cylinder bores 28 .
- the three rear block-side discharge chambers 42 are located around the rotary shaft 22 and each rear block-side discharge chamber 42 is located between any two adjacent rear cylinder bores 29 .
- the front block-side discharge chambers 40 are formed on the outer circumference side of the front suction chambers 17 in the radial direction of the front cylinder block 11 and the rear block-side discharge chambers 42 are formed on the outer circumference side of the rear suction chambers 18 in the radial direction of the rear cylinder block 12 .
- the front and the rear block-side discharge chambers 40 and 42 serve as a block-side discharge chamber of the present invention.
- Front discharge ports 15 A are formed in the front valve plate assembly 15 at positions facing the corresponding front cylinder bores 28 and rear discharge ports 16 A are formed in the rear valve plate assembly 16 at positions facing the corresponding rear cylinder bores 29 .
- Front discharge valves 15 B are formed in the front valve plate 20 at positions facing the corresponding front discharge ports 15 A and rear discharge valves 16 B are formed in the rear valve plate 21 at positions facing the corresponding rear discharge ports 16 A.
- Front retainers 15 C are formed in the front valve plate assembly 15 to regulate the opening degrees of the front discharge valves 15 B, respectively and rear retainers 16 C are formed in the rear valve plate assembly 16 to regulate the opening degrees of the rear discharge valves 16 B, respectively.
- the front discharge ports 15 A communicate with the first through the third front head-side discharge chambers 33 A through 33 C, respectively, and the rear discharge ports 16 A communicate with the first through the third rear head-side discharge chambers 35 A through 35 C, respectively.
- Refrigerant gas flowed from the front compression chamber 28 A is flowed to the first through the third front head-side discharge chambers 33 A through 33 C and refrigerant gas flowed from the rear compression chamber 29 A is flowed to the first through the third rear head-side discharge chambers 35 A through 35 C.
- the front and the rear discharge ports 15 A and 16 A serve as a discharge port of the present invention.
- the front and the rear retainer 15 C and 16 C serve as a retainer of the present invention.
- a suction passage 43 is formed in the front and the rear cylinder blocks 11 and 12 .
- the opening of the front end of the suction passage 43 communicates with the front suction chambers 17 with the largest volume among three front suction chambers 17 .
- the opening of the rear end of the suction passage 43 communicates with the rear suction chamber 18 with the largest volume among three rear suction chambers 18 .
- An inlet 44 is formed in the front cylinder block 11 . One end of the inlet 44 is opened through the front cylinder block 11 and the other end of the inlet 44 is opened to the suction passage 43 .
- An external refrigerant circuit disposed outside of the compressor 10 is connected to the opening of the one end of the inlet 44 .
- the suction passage 43 is formed to communicate the front and the rear suction chambers 17 and 18 each of which has the largest volume on the front and the rear sides among the front and the rear suction chambers 17 and 18 . Therefore, the suction passage 43 is interposed in the axial direction between the front and the rear block-side discharge chambers 40 and 42 located on the outer circumference side of the front and the rear suction chambers 17 and 18 .
- a discharge passage 45 is formed in the front and the rear cylinder blocks 11 and 12 .
- the opening of the front end of the discharge passage 45 communicates with one of three front block-side discharge chambers 40 and the opening of the rear end of the discharge passage 45 communicates with one of three rear block-side discharge chambers 42 .
- an outlet 46 is formed through the front cylinder block 11 , or housing H. One end of the outlet 46 is opened through the front cylinder block 11 (the housing H) and the other end of the outlet 46 is opened to the discharge passage 45 .
- the external refrigerant circuit provided outside of the compressor 10 is connected to the outlet 46 . As shown in FIG.
- the discharge passage 45 is formed in the front and the rear cylinder blocks 11 and 12 at a position shifted in the rotating direction of the front and the rear cylinder blocks 11 and 12 from the suction passage 43 .
- the front compression chambers 28 A communicate with the discharge passage 45 through the first through the third front head-side discharge chambers 33 A through 33 C and the front block-side discharge chambers 40 .
- the rear compression chambers 29 A communicates with the discharge passage 45 through the rear head-side discharge chambers 35 A through 35 C and the rear block-side discharge chambers 42 .
- a discharge path extending from the front and the rear compression chambers 28 A and 29 A to the outlet 46 through the first through the third front head-side discharge chambers 33 A through 33 C and the first through the third rear head-side discharge chambers 35 A through 35 C, the front and the rear block-side discharge chambers 40 and 42 and the discharge passage 45 is formed in the housing H.
- the external refrigerant circuit connects the outlet 46 with the inlet 44 of the compressor 10 .
- the external refrigerant circuit includes a condenser, an expansion valve and an evaporator, which are arranged in the external refrigerant circuit in this order from the outlet 46 of the compressor 10 .
- communication passages 50 A are formed in the front cylinder blocks 11 for respectively communicating the front suction chambers 17 with the front shaft hole 11 A.
- One ends of the communication passages 50 A are opened to the front suction chambers 17 and the other ends of the communication passages 50 A are opened to the front shaft hole 11 A at the sealing circumferential surface thereof.
- the communication passages 50 A are formed in the front cylinder block 11 so as to extend while slightly tilting in the radial direction of the front cylinder block 11 .
- Introducing passages 50 B are formed in the front cylinder block 11 for respectively communicating the front shaft hole 11 A with the front cylinder bores 28 .
- One ends of the introducing passages 50 B are opened to the front shaft hole 11 A at the sealing circumferential surface thereof and the other ends of the introducing passages 50 B are opened to the front cylinder bores 28 .
- the communication passages 50 A and the introducing passages 50 B are alternately arranged in the rotating direction of the rotary shaft 22 .
- the communication passages 50 A and the introducing passages 50 B are opened to the front shaft hole 11 A at the same position in the axial direction of the front shaft hole 11 A.
- a front groove 22 A is formed on the circumferential surface of the rotary shaft 22 on the front side.
- the front groove 22 A is recessed on the circumferential surface of the rotary shaft 22 on the front cylinder head 13 side.
- the front groove 22 A is opened to the front shaft hole 11 A at the sealing circumferential surface and communicable with the communication passage 50 A and the introducing passage 50 B.
- the position of the front groove 22 A is changed to mechanically switch communication paths between communication passage 50 A and the introducing passage 50 B and the front groove 22 A.
- a portion of the rotary shaft 22 surrounded by the sealing circumferential surface is a front rotary valve RF which is integrally formed with the rotary shaft 22 .
- the front groove 22 A is configured to communicate one communication passage 50 A with one introducing passage 50 B located adjacent to the communication passage 50 A in the rotating direction of the rotary shaft 22 .
- the communication passage 50 A communicates with the introducing passage 50 B through the front groove 22 A in accordance with the rotation of the rotary shaft 22 , so that the refrigerant gas is flowed from the front suction chamber 17 into the front cylinder bore 28 adjacent to the front suction chamber 17 .
- introducing passages 51 are formed in the rear cylinder block 12 for respectively communicating the rear cylinder bores 29 with the rear shaft hole 12 A.
- One ends of the introducing passages 51 are opened to the rear cylinder bores 29 , respectively, and the other ends of the introducing passages 51 are opened to the rear shaft hole 12 A at the sealing circumferential surface.
- a rear supply passage 22 B is formed on the circumferential surface of the rear end of the rotary shaft 22 .
- One end of the rear supply passage 22 B is opened to a cylinder suction chamber 19 formed in the rear cylinder head 14 and the other end of the rear supply passage 22 B is communicable with the other end of the introducing passages 51 .
- the position of the rear supply passage 22 B is changed to mechanically switch communication paths between the introducing passages 51 and the rear supply passage 22 B. Therefore, a portion of the rotary shaft 22 surrounded by the sealing circumferential surface is a rear rotary valve RR which is integrally formed with the rotary shaft 22 .
- the cylinder suction chamber 19 serves as the suction chamber of the present invention.
- the front space 28 B is recessed on the front cylinder head 13 so as to annularly surround the rotary shaft 22 .
- First through third front partition walls 32 A through 32 C are provided in the front cylinder head 13 for dividing the front space 28 B into the first through the third front head-side discharge chambers 33 A through 33 C.
- the first through the third front partition walls 32 A through 32 C extend from the bottom surface of the front cylinder head 13 toward the front block-side discharge chambers 40 .
- the first front partition wall 32 A is provided at a position adjacent to the front block-side discharge chamber 40 , which communicates with the discharge passage 45 , in the rotating direction of the rotary shaft 22 .
- the first and the second front partition walls 32 A and 32 B are disposed adjacent to each other so as to interpose one front cylinder bore 28 in the rotating direction of the rotary shaft 22 .
- the front space 28 B includes the first front head-side discharge chamber 33 A which is formed by the first and the second front partition walls 32 A and 32 B.
- the first front head-side discharge chamber 33 A communicates with one front cylinder bore 28 (the front compression chamber 28 A) through one front discharge port 15 A.
- the second and the third front partition walls 32 B and 32 C are disposed adjacent to each other so as to interpose another front cylinder bore 28 in the rotating direction of the rotary shaft 22 .
- the front space 28 B includes the second front head-side discharge chamber 33 B formed by the second and the third front partition walls 32 B and 32 C.
- the second front head-side discharge chamber 33 B communicates with one front cylinder bore 28 (the front compression chamber 28 A), which is different from the front cylinder bore 28 communicating with the first front head-side discharge chamber 33 A, through one front discharge port 15 A.
- the front space 28 B includes the third front head-side discharge chamber 33 C formed by the first and the third front partition walls 32 A and 32 C.
- the third front head-side discharge chamber 33 C communicates with the remaining one front cylinder bore 28 (the front compression chamber 28 A) through one front discharge port 15 A.
- the third front head-side discharge chamber 33 C communicates with the discharge passage 45 through the front block-side discharge chamber 40 .
- a rear space 29 B is recessed on the rear cylinder head 14 so as to annularly surround the rotary shaft 22 .
- First through third rear partition walls 34 A through 34 C are provided in the rear cylinder head 14 for dividing the rear space 29 B into three spaces.
- the first through the third rear partition walls 34 A through 34 C extend from the bottom surface of the rear cylinder head 14 toward the rear block-side discharge chamber 42 .
- the first rear partition wall 34 A is provided at a position adjacent to the rear block-side discharge chamber 42 , which communicates with the discharge passage 45 , in the rotating direction of the rotary shaft 22 .
- the first and the second rear partition walls 34 A and 34 B are provided adjacent to each other so as to interpose one rear cylinder bore 29 in the rotating direction of the rotary shaft 22 .
- the rear space 29 B includes the first rear head-side discharge chamber 35 A formed by the first and the second rear partition walls 34 A and 34 B.
- the first rear head-side discharge chamber 35 A communicates with one rear cylinder bore 29 (the rear compression chamber 29 A) through one rear discharge port 16 A.
- the second and the third rear partition walls 34 B and 34 C are provided adjacent to each other so as to interpose another rear cylinder bore 29 in the rotating direction of the rotary shaft 22 .
- the rear space 29 B includes the second rear head-side discharge chamber 35 B formed by the second and the third rear partition walls 34 B and 34 C.
- the second rear head-side discharge chamber 35 B communicates with one rear cylinder bore 29 (the rear compression chamber 29 A) which is different from the rear cylinder bore 29 communicating with the first rear head-side discharge chamber 35 A through one rear discharge port 16 A.
- the rear space 29 B further includes the third rear head-side discharge chamber 35 C formed by the first and the third rear partition walls 34 C and 34 A.
- the third rear head-side discharge chamber 35 C communicates with the remaining one rear cylinder bore 29 (the rear compression chamber 29 A) through one rear discharge port 16 A.
- the third rear head-side discharge chamber 35 C communicates with the discharge passage 45 through the rear block-side discharge chamber 42 .
- first front throttles 15 F are formed in the gasket G of the front valve plate assembly 15 so as to interpose the second front partition wall 32 B and the third front partition wall 32 C, respectively.
- Two pairs of first rear throttles 16 F are formed in the gasket G of the rear valve plate assembly 16 so as to interpose the second and the third rear partition walls 34 B and 34 C, respectively.
- Two pairs of second front throttles 20 A are formed in the front valve plate 20 for communicating with the first front throttles 15 F, respectively.
- Two pairs of second rear throttles 21 A are formed in the rear valve plate 21 for communicating with the first rear throttles 16 F, respectively.
- the first and the second front head-side discharge chambers 33 A and 33 B communicate through one front block-side discharge chamber 40 with the pairs of first and second front throttles 15 F and 20 A which interpose the second front partition wall 32 B.
- the first and the second rear head-side discharge chambers 35 A and 35 B communicate through one rear block-side discharge chamber 42 with the pairs of first and the second rear throttles 16 F and 21 A which interpose the second rear partition wall 34 B.
- the second and the third front head-side discharge chambers 33 B and 33 C communicate through the other front block-side discharge chamber 40 with the pairs of the first and the second front throttles 15 F and 20 A which interpose the third front partition wall 32 C.
- the second and the third rear head-side discharge chambers 35 B and 35 C communicate through the other rear block-side discharge chamber 42 with the pairs of the first and the second rear throttles 16 F and 21 A which interpose the third rear partition wall 34 C.
- the first and the third front head-side discharge chambers 33 A and 33 C are separated by the first front partition wall 32 A and do not communicate with each other.
- the first and the third rear head-side discharge chambers 35 A and 35 C are separated by the first rear partition wall 34 A and do not communicate with each other.
- refrigerant gas flows in the rotating direction of the rotary shaft 22 from the first front head-side discharge chamber 33 A to the second front head-side discharge chamber 33 B and then to the third front head-side discharge chamber 33 C, as indicated by the arrows Y in FIG. 3 .
- refrigerant gas flows in the rotating direction of the rotary shaft 22 from the first rear head-side discharge chamber 35 A to the second rear head-side discharge chamber 35 B and then to the third rear head-side discharge chamber 35 C, as indicated by the arrows Y in FIG. 7 .
- the first front throttle 15 F and the first rear throttle 16 F serve as a first throttle of the present invention.
- the second front throttle 20 A and the second rear throttle 21 A serve as a second throttle of the present invention.
- the refrigerant gas is flowed into the suction passage 43 through the inlet 44 and supplied to the front and the rear suction chambers 17 and 18 .
- the refrigerant gas is flowed into the suction passage 43 through the inlet 44 and supplied to the front and the rear suction chambers 17 and 18 .
- one communication passage 50 A and the introducing passage 50 B adjacent to the communication passage 50 A communicate with each other through the front groove 22 A of the front rotary valve RF.
- the refrigerant gas is flowed into the front cylinder bores 28 from the front suction chamber 17 through the front rotary valve RF.
- the front groove 22 A is disconnected from the communication passage 50 A, the communication of the communication passage 50 A and the introducing passage 50 B is blocked, and the front cylinder bores 28 are shut off.
- the front cylinder bores 28 shift to a compression stroke and a discharge stroke.
- the refrigerant gas discharged to the first front head-side discharge chamber 33 A passes through one second front throttle 20 A and one first front throttle 15 F formed across the second front partition wall 32 B along the axial direction of the rotary shaft 22 and flows into the front block-side discharge chamber 40 . Then, the refrigerant gas passes through the other first front throttle 15 F and the other second front throttle 20 A along the axial direction of the rotary shaft 22 and flows to the second front head-side discharge chamber 33 B different from the first front head-side discharge chamber 33 A.
- the refrigerant gas discharged from the front compression chamber 28 A facing the second front head-side discharge chamber 33 B passes through one pair of the second front throttle 20 A and the first front throttle 15 F formed across the third front partition wall 32 C in the axial direction of the rotary shaft 22 and flows into the front block-side discharge chamber 40 together with the refrigerant gas flowed from the first front head-side discharge chamber 33 A. Then, the refrigerant gas passes through the other first front throttle 15 F and the other second front throttle 20 A from the front block-side discharge chamber 40 in the axial direction of the rotary shaft 22 and flows to the third front head-side discharge chamber 33 C different from the second front head-side discharge chamber 33 B.
- the refrigerant gas discharged from the front compression chamber 28 A facing the third front head-side discharge chamber 33 C into the third front head-side discharge chamber 33 C is flowed into the front block-side discharge chamber 40 and, then, flowed out to the external refrigerant circuit through the discharge passage 45 and the outlet 46 together with the refrigerant gas flowed from the second front head-side discharge chamber 33 B.
- the rear supply passage 22 B communicating with the cylinder suction chamber 19 in the rear rotary valve RR communicates with one introducing passage 51 . Then, the refrigerant gas is supplied to the introducing passage 51 from the cylinder suction chamber 19 through the rear rotary valve RR and flowed into the rear cylinder bore 29 communicating with the introducing passage 51 .
- the rear supply passage 22 B is disconnected from the introducing passage 51 , the communication between the introducing passage 51 and the cylinder suction chamber 19 is blocked, and the rear cylinder bores 29 is shut off.
- the rear cylinder bores 29 shift to the compression stroke and the discharge stroke.
- the refrigerant gas discharged to the first rear head-side discharge chamber 35 A passes through one second rear throttle 21 A and one first rear throttle 16 F formed across the second rear partition wall 34 B in the axial direction of the rotary shaft 22 and is flowed into the rear block-side discharge chamber 42 . Then, the refrigerant gas in the rear block-side discharge chamber 42 passes the other first rear throttle 16 F and the other second rear throttle 21 A in the axial direction of the rotary shaft 22 and flows into the second rear head-side discharge chamber 35 B different from the first rear head-side discharge chamber 35 A.
- the refrigerant gas discharged from the rear compression chamber 29 A facing the second rear head-side discharge chamber 35 B passes through one second rear throttle 21 A and one first rear throttle 16 F formed across the third rear partition wall 34 C in the axial direction of the rotary shaft 22 and flows into the rear block-side discharge chamber 42 together with the refrigerant gas flowing from the first rear head-side discharge chamber 35 A. Then, the refrigerant gas in the rear block-side discharge chamber 42 passes through the other first rear throttle 16 F and the other second rear throttle 21 A in the axial direction of the rotary shaft 22 and flows into the third rear head-side discharge chamber 35 C which is different from the second rear head-side discharge chamber 35 B.
- the refrigerant gas discharged to the third rear head-side discharge chamber 35 C flows into the rear block-side discharge chamber 42 , flows through the discharge passage 45 , and is discharged from the outlet 46 together with the refrigerant gas flowing from the second rear head-side discharge chamber 35 B.
- the refrigerant gas discharged from the front and the rear compression chambers 28 A and 29 A may be reciprocated for a plurality of times by using the first through the third front head-side discharge chambers 33 A through 33 C and the first through the third rear head-side discharge chambers 35 A through 35 C and the front and the rear block-side discharge chambers 40 and 42 . Therefore, the refrigerant gas is made to meander until the discharged refrigerant gas is discharged from the outlet 46 .
- the above preferred embodiment may be modified into various alternative embodiments, as exemplified below.
- the diameter of the first front throttles 15 F and the first rear throttles 16 F and the second front throttles 20 A and the second rear throttles 21 A may be changed.
- the front and the rear discharge ports 15 A and 16 A may be formed in other than the front and the rear valve plate assemblies 15 and 16 .
- Only the gaskets G may be provided between the front and the rear cylinder blocks 11 and 12 and the front and the rear cylinder heads 13 and 14 , respectively, and the front and the rear discharge ports 15 A and 16 A and the first front throttles 15 F and the first rear throttles 16 F may be provided in the gaskets G, respectively.
- the front and the rear block-side discharge chambers 40 and 42 do not have to be provided one by one in the gaps of the front and the rear cylinder bores 28 and 29 adjacent to one another. In some of the gaps, the front and the rear block-side discharge chambers 40 and 42 may be not provided.
- partition walls may be provided in each of the front and the rear cylinder heads 13 and 14 and four or more front block-side discharge chambers 40 and four or more rear block-side discharge chambers 42 may be provided to increase the number of times of the reciprocation of the refrigerant gas.
- two partition walls may be provided in each of the front and the rear cylinder heads 13 and 14 and two or more front block-side discharge chambers 40 and two or more rear block-side discharge chambers 42 may be provided to reduce the number of times of reciprocation of the refrigerant gas.
- the outlet 46 is opened through the front cylinder block 11 .
- an outlet may be formed to be opened through the rear cylinder block 12 , or the front and the rear cylinder heads 13 and 14 .
- the rotary valves are adapted to suctioning on the front and the rear sides of the compressor 10 .
- suction valves may be adapted to suctioning on the front and the rear sides in stead of the rotary valves.
- the refrigerant gas in the front suction chambers 18 is collected in the cylinder suction chamber 19 and is flowed into the rear cylinder bores 29 from the cylinder suction chamber 19 through the rear rotary valve RR.
- the rear suction chambers 18 and the rear shaft hole 12 A may communicate through communication passages and introducing grooves
- the rear shaft hole 12 A and the rear cylinder bores 29 may separately communicate through introducing passages, respectively.
- the refrigerant gas may be flowed into the rear cylinder bores 29 from the rear suction chambers 18 through the communication passages, the introducing grooves of the rear rotary valve RR and the introducing passages.
- the refrigerant gas passed through the inlet 44 is supplied to the front and the rear compression chambers 28 A and 29 A through the front groove 22 A and the rear supply passage 22 B formed on the surface of the rotary shaft 22 .
- a rotary shaft may be formed to include an inner passage therein as a hollow shaft.
- the refrigerant gas flowed through the inlet 44 is supplied to the front and the rear suction chambers 17 and 18 through the suction passage 43 formed in the front and the rear cylinder blocks 11 and 12 .
- the refrigerant gas flowed through the inlet 44 may be supplied to the front and the rear suction chambers 17 and 18 through the crank chamber 25 .
- the volume of one front suction chamber 17 and one rear suction chamber 18 which communicate with the suction passage 43 is set larger than the volume of the other two front suction chambers 17 and the other two rear suction chambers 18 .
- the volume of the other two front suction chambers 17 and the other two rear suction chambers 18 may be set larger than the volume of the front and the rear suction chambers 17 and 18 which communicate with the suction passage 43 .
- the three front suction chambers 17 may have the same volume and also three rear suction chambers 18 may have the same volume.
- Only one front block-side discharge chamber 40 may be provided and each front space 28 B may be partitioned into two front head-side discharge chambers.
- Only one rear block-side discharge chamber 42 may be provided and each rear space 29 B may be partitioned into two rear head-side discharge chambers.
- the number of the front and the rear cylinder bores 28 and 29 may be changed.
- the compressor 10 is a double-headed piston type swash plate compressor including the double-headed pistons 30 .
- the piston type swash plate compressor may be a single-headed piston type swash plate compressor including a single-headed piston.
Abstract
A piston type swash plate compressor includes a housing, a cylinder block, a cylinder head, a rotary shaft, a plurality of cylinder bores, a plurality of pistons, a swash plate, a plurality of compression chambers, a plurality of head-side discharge chambers, a plurality of block-side discharge chambers, an outlet and a discharge path. The head-side discharge chambers are provided in the cylinder head. The block-side discharge chambers are provided in the cylinder block. The outlet is formed through the housing. The discharge path is formed in the housing and refrigerant gas is flowed through the discharge path from the compression chamber to the outlet through the head-side discharge chamber to the block-side discharge chamber. After refrigerant gas flowed from the compression chamber is flowed through one head-side discharge chamber which communicates with the compression chamber and one block-side discharge chamber, the refrigerant gas is flowed to another head-side discharge chamber.
Description
- The present invention relates to a piston type swash plate compressor.
- In a piston type swash plate compressor, refrigerant gas is introduced into compression chambers and compressed and discharged by reciprocation motion of pistons together with rotation of a swash plate. In the piston type swash plate compressor, vibration and noise development are caused by pulsation of refrigerant gas. There has been proposed a compressor including a muffler for reducing the pulsation. For example, Japanese Patent Application Publication No. 10-89251 discloses a compressor wherein a muffler space is formed in a compressor housing, a compression chamber is connected to the muffler space and a meandering member is provided in the muffler space for defining a passage for meandering discharged gas.
- However, if the muffler space is formed in the piston type swash plate compressor in order to reduce the pulsation as in Japanese Patent Application Publication No. 10-89251, the compressor housing extends outwardly and the size of the piston type swash plate compressor is increased. The present invention, which has been made in light of the above problems, is directed to providing a piston type swash plate compressor which can reduce the pulsation without being large in size.
- In accordance with the present invention, a piston type swash plate compressor includes a housing, a cylinder block, a cylinder head, a rotary shaft, a plurality of cylinder bores, a plurality of pistons, a swash plate, a plurality of compression chambers, a plurality of head-side discharge chambers, a plurality of block-side discharge chambers, an outlet and a discharge path. The cylinder block is formed in the housing. The cylinder head is formed in the housing and connected to an end of the cylinder block. The rotary shaft is rotatably supported by the cylinder block. A plurality of cylinder bores is arranged around the rotary shaft. A plurality of pistons is respectively accommodated in the cylinder bores. The swash plate integrally rotates with the rotary shaft and is engaged with the pistons. A plurality of the compression chambers is respectively defined in the cylinder bores by the pistons. A plurality of the head-side discharge chambers is provided in the cylinder head. A plurality of the block-side discharge chambers is provided in the cylinder block. The outlet is formed in the housing and compressed refrigerant gas is flowed outside of the housing through the outlet. The discharge path is formed in the housing and refrigerant gas is flowed through the discharge path from the compression chamber to the outlet to the block-side discharge chamber through the head-side discharge chamber. After refrigerant gas flowed from the compression chamber is flowed through one head-side discharge chamber which communicates with the compression chamber and one block-side discharge chamber, the refrigerant gas is flowed to another head-side discharge chamber.
- Other aspects and advantages of the 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 sectional view taken along the line I-I inFIG. 3 showing a double-headed piston type swash plate compressor according to a first preferred embodiment of the present invention; -
FIG. 2 is a sectional view taken along the line II-II inFIG. 3 showing the double-headed piston type swash plate compressor ofFIG. 1 ; -
FIG. 3 is a sectional view taken along the line inFIG. 1 showing front head-side discharge chambers and front suction chambers of the double-headed piston type swash plate compressor ofFIG. 1 ; -
FIG. 4 is a sectional view taken along the line IV-IV inFIG. 1 showing front block-side discharge chambers and the front suction chambers of the double-headed piston type swash plate compressor ofFIG. 1 ; -
FIG. 5 is a sectional view taken along the line V-V inFIG. 1 showing the front head-side discharge chambers and front partition walls of the double-headed piston type swash plate compressor ofFIG. 1 ; -
FIG. 6 is a sectional view showing the front head-side discharge chambers, front compression chambers and the front block-side discharge chambers expanded in a rotating direction of a rotary shaft of the double-headed piston type swash plate compressor ofFIG. 1 ; and -
FIG. 7 is a sectional view taken along the line VII-VII inFIG. 1 showing the rear head-side discharge chambers and rear partition walls of the double-headed piston type swash plate compressor ofFIG. 1 . - The following will describe a piston type swash plate compressor embodied as a double-headed piston type swash plate compressor according to a preferred embodiment of the present invention with reference to
FIGS. 1 through 7 . As shown inFIGS. 1 and 2 ,reference numeral 10 designates a double-headed piston type swash plate compressor (hereinafter simply referred to as “compressor”) and thecompressor 10 includes a housing H and a pair of front andrear cylinder blocks compressor 10, afront cylinder head 13 is disposed on the front side of the compressor 10 (the left side inFIG. 1 ) and coupled to the front end of thefront cylinder block 11 through the frontvalve plate assembly 15. The frontvalve plate assembly 15 includes a gasket G for sealing a space between thefront cylinder block 11 and thefront cylinder head 13 and a valve plate 20 a part of which forms afront discharge valve 15B which will be describe later. Arear cylinder head 14 is disposed on a rear side of the compressor 10 (the right side inFIG. 1 ) and coupled to the rear end of therear cylinder block 12 through a rearvalve plate assembly 16. The rearvalve plate assembly 16 includes the gasket G for sealing a space between therear cylinder block 12 and therear cylinder head 14 and a rear valve plate 21 a part of which forms arear discharge valve 16B which will be described later. The front and therear cylinder heads rear cylinder blocks rear cylinder heads rear cylinder blocks rear cylinder heads rear discharge valves rear valve plates - The front and the
rear cylinder blocks rear shaft holes rotary shaft 22 is inserted through the front and therear shaft holes rear shaft holes rear insertion holes rotary shaft 22 is inserted through the front and therear insertion holes shaft seal 23 of a lip seal type hermetically seals a space between the outer circumferential surface of the front end of therotary shaft 22 extending out of the frontvalve plate assembly 15 and the inner circumferential surface of thefront cylinder head 13. Theshaft seal 23 is provided in anaccommodation chamber 13C formed between the inner circumferential surface of thefront cylinder head 13 and the outer circumferential surface of therotary shaft 22. The front and therear shaft holes rear insertion holes - A
swash plate 24, which integrally rotates with therotary shaft 22, is firmly fixed to therotary shaft 22. Theswash plate 24 is disposed in acrank chamber 25 formed between the front and therear cylinder blocks front cylinder block 11 and anannular base portion 24A of theswash plate 24. A rear thrust bearing 27 is interposed between the front end surface of therear cylinder block 12 and thebase portion 24A of theswash plate 24. The front and therear thrust bearings swash plate 24 and regulate the movement of theswash plate 24 along the center axis L of therotary shaft 22. The front and therear thrust bearings - As shown in
FIG. 4 , threefront cylinder bores 28 are arranged around therotary shaft 22 in thefront cylinder block 11. As shown inFIG. 1 , threerear cylinder bores 29 are arranged around therotary shaft 22 in therear cylinder block 12. The paired front andrear cylinder bores headed pistons 30 are received in the front and the rear cylinder bores 28 and 29, respectively. Thefront cylinder bore 28 is closed by the frontvalve plate assembly 15 and the double-headed piston 30 and therear cylinder bore 29 is closed by the rearvalve plate assembly 16 and the double-headed piston 30. The front and the rear cylinder bores 28 and 29 serve as a cylinder bore of the present invention. - The rotating movement of the
swash plate 24 which integrally rotates with therotary shaft 22 is transmitted to the double-headed pistons 30 through a pair ofshoes 31 which hold theswash plate 24 from opposite sides thereof. The double-headed pistons 30 are reciprocally moved in the front and the rear cylinder bores 28 and 29. Afront compression chamber 28A is defined in thefront cylinder bore 28 by the double-headed piston 30 and the frontvalve plate assembly 15 and arear compression chamber 29A is defined in therear cylinder bore 29 by the double-headed piston 30 and the rearvalve plate assembly 16. The front and therear compression chambers - As shown in
FIGS. 1 and 4 , threefront suction chambers 17 and threerear suction chambers 18 are formed surrounding therotary shaft 22 and extending through the front and the rearvalve plate assemblies rear cylinder heads rear cylinder blocks front suction chamber 17 is located between any two adjacent front cylinder bores 28 and eachrear suction chamber 18 is located between any two adjacent rear cylinder bores 29. The front and therear suction chambers rear shaft holes front suction chamber 17 has a length in the axial direction of therotary shaft 22 and a volume larger than the length and the volume of the otherfront suction chamber 17 and onerear suction chamber 18 has a length in the axial direction of therotary shaft 22 and a volume larger than the length and the volume of the otherrear suction chamber 18. The front and therear suction chambers - As shown in
FIGS. 1 and 3 , in thefront cylinder head 13, each of the threefront suction chambers 17 communicates with theaccommodation chamber 13C and threefront suction chambers 17 communicate with each other through theaccommodation chamber 13C. Thus, the threefront suction chambers 17 and theaccommodation chamber 13C form one space. - As shown in
FIGS. 1 , 3 and 7, three first through third front head-side discharge chambers 33A through 33C are located so as to surround therotary shaft 22 between thefront cylinder head 13 and the frontvalve plate assembly 15 and three first through third rear head-side discharge chambers 35A through 35C are located so as to surround therotary shaft 22 between therear cylinder head 14 and the rearvalve plate assembly 16. Refrigerant gas flowed from the front and therear compression chambers side discharge chambers 33A through 33C and the first through the third rear head-side discharge chambers 35A through 35C, respectively. Afront space 28B is formed around therotary shaft 22 in thefront cylinder head 13 and partitioned to the first through the third front head-side discharge chambers 33A through 33C. Arear space 29B is formed around therotary shaft 22 in therear cylinder head 14 and partitioned to the first through the third rear head-side discharge chambers 35A through 35C. The size of the openings of the first through the third front head-side discharge chambers 33A through 33C and the first through the third rear head-side discharge chambers 35A through 35C at positions facing the front and therear compression chambers valve plate assemblies rear compression chambers side discharge chambers 33A through 33C and the first through the third rear head-side discharge chambers 35A through 35C serve as a head-side discharge chamber of the present invention. The front and therear spaces - Three front block-
side discharge chambers 40 are formed in thefront cylinder block 11 and three rear block-side discharge chambers 42 are formed in therear cylinder block 12. Thefront compression chambers 28A, the first through the third front head-side discharge chambers 33A through 33C and the front block-side discharge chambers 40 communicate with one another and therear compression chambers 29A, the first through the third rear head-side discharge chambers 35A through 35C and the rear block-side discharge chambers 42 communicate with one another. The three front block-side discharge chambers 40 are located around therotary shaft 22 and each front block-side discharge chamber 40 is located between any two adjacent front cylinder bores 28. The three rear block-side discharge chambers 42 are located around therotary shaft 22 and each rear block-side discharge chamber 42 is located between any two adjacent rear cylinder bores 29. The front block-side discharge chambers 40 are formed on the outer circumference side of thefront suction chambers 17 in the radial direction of thefront cylinder block 11 and the rear block-side discharge chambers 42 are formed on the outer circumference side of therear suction chambers 18 in the radial direction of therear cylinder block 12. The front and the rear block-side discharge chambers -
Front discharge ports 15A are formed in the frontvalve plate assembly 15 at positions facing the corresponding front cylinder bores 28 andrear discharge ports 16A are formed in the rearvalve plate assembly 16 at positions facing the corresponding rear cylinder bores 29.Front discharge valves 15B are formed in thefront valve plate 20 at positions facing the correspondingfront discharge ports 15A andrear discharge valves 16B are formed in therear valve plate 21 at positions facing the correspondingrear discharge ports 16A.Front retainers 15C are formed in the frontvalve plate assembly 15 to regulate the opening degrees of thefront discharge valves 15B, respectively andrear retainers 16C are formed in the rearvalve plate assembly 16 to regulate the opening degrees of therear discharge valves 16B, respectively. Thefront discharge ports 15A communicate with the first through the third front head-side discharge chambers 33A through 33C, respectively, and therear discharge ports 16A communicate with the first through the third rear head-side discharge chambers 35A through 35C, respectively. Refrigerant gas flowed from thefront compression chamber 28A is flowed to the first through the third front head-side discharge chambers 33A through 33C and refrigerant gas flowed from therear compression chamber 29A is flowed to the first through the third rear head-side discharge chambers 35A through 35C. The front and therear discharge ports rear retainer - As shown in
FIG. 1 , asuction passage 43 is formed in the front and therear cylinder blocks suction passage 43 communicates with thefront suction chambers 17 with the largest volume among threefront suction chambers 17. The opening of the rear end of thesuction passage 43 communicates with therear suction chamber 18 with the largest volume among threerear suction chambers 18. Aninlet 44 is formed in thefront cylinder block 11. One end of theinlet 44 is opened through thefront cylinder block 11 and the other end of theinlet 44 is opened to thesuction passage 43. An external refrigerant circuit disposed outside of thecompressor 10 is connected to the opening of the one end of theinlet 44. - The
suction passage 43 is formed to communicate the front and therear suction chambers rear suction chambers suction passage 43 is interposed in the axial direction between the front and the rear block-side discharge chambers rear suction chambers - As shown in
FIG. 2 , adischarge passage 45 is formed in the front and therear cylinder blocks discharge passage 45 communicates with one of three front block-side discharge chambers 40 and the opening of the rear end of thedischarge passage 45 communicates with one of three rear block-side discharge chambers 42. Further, anoutlet 46 is formed through thefront cylinder block 11, or housing H. One end of theoutlet 46 is opened through the front cylinder block 11 (the housing H) and the other end of theoutlet 46 is opened to thedischarge passage 45. The external refrigerant circuit provided outside of thecompressor 10 is connected to theoutlet 46. As shown inFIG. 3 , thedischarge passage 45 is formed in the front and therear cylinder blocks rear cylinder blocks suction passage 43. Thefront compression chambers 28A communicate with thedischarge passage 45 through the first through the third front head-side discharge chambers 33A through 33C and the front block-side discharge chambers 40. Therear compression chambers 29A communicates with thedischarge passage 45 through the rear head-side discharge chambers 35A through 35C and the rear block-side discharge chambers 42. Therefore, a discharge path extending from the front and therear compression chambers outlet 46 through the first through the third front head-side discharge chambers 33A through 33C and the first through the third rear head-side discharge chambers 35A through 35C, the front and the rear block-side discharge chambers discharge passage 45 is formed in the housing H. - In a case that the
compressor 10 is used in a refrigerant circuit for a vehicle air-conditioner, the external refrigerant circuit connects theoutlet 46 with theinlet 44 of thecompressor 10. The external refrigerant circuit includes a condenser, an expansion valve and an evaporator, which are arranged in the external refrigerant circuit in this order from theoutlet 46 of thecompressor 10. - The following will describe a suction structure in the
compressor 10. As shown inFIGS. 1 and 4 ,communication passages 50A are formed in thefront cylinder blocks 11 for respectively communicating thefront suction chambers 17 with thefront shaft hole 11A. One ends of thecommunication passages 50A are opened to thefront suction chambers 17 and the other ends of thecommunication passages 50A are opened to thefront shaft hole 11A at the sealing circumferential surface thereof. Thecommunication passages 50A are formed in thefront cylinder block 11 so as to extend while slightly tilting in the radial direction of thefront cylinder block 11. - Introducing
passages 50B are formed in thefront cylinder block 11 for respectively communicating thefront shaft hole 11A with the front cylinder bores 28. One ends of the introducingpassages 50B are opened to thefront shaft hole 11A at the sealing circumferential surface thereof and the other ends of the introducingpassages 50B are opened to the front cylinder bores 28. Thecommunication passages 50A and the introducingpassages 50B are alternately arranged in the rotating direction of therotary shaft 22. Thecommunication passages 50A and the introducingpassages 50B are opened to thefront shaft hole 11A at the same position in the axial direction of thefront shaft hole 11A. - A
front groove 22A is formed on the circumferential surface of therotary shaft 22 on the front side. Thefront groove 22A is recessed on the circumferential surface of therotary shaft 22 on thefront cylinder head 13 side. Thefront groove 22A is opened to thefront shaft hole 11A at the sealing circumferential surface and communicable with thecommunication passage 50A and the introducingpassage 50B. In accordance with the rotation of therotary shaft 22, the position of thefront groove 22A is changed to mechanically switch communication paths betweencommunication passage 50A and the introducingpassage 50B and thefront groove 22A. - Therefore, a portion of the
rotary shaft 22 surrounded by the sealing circumferential surface is a front rotary valve RF which is integrally formed with therotary shaft 22. Thefront groove 22A is configured to communicate onecommunication passage 50A with one introducingpassage 50B located adjacent to thecommunication passage 50A in the rotating direction of therotary shaft 22. Thecommunication passage 50A communicates with the introducingpassage 50B through thefront groove 22A in accordance with the rotation of therotary shaft 22, so that the refrigerant gas is flowed from thefront suction chamber 17 into the front cylinder bore 28 adjacent to thefront suction chamber 17. - The following will describe a suction structure on the rear side of the
compressor 10. As shown inFIGS. 1 and 2 , introducingpassages 51 are formed in therear cylinder block 12 for respectively communicating the rear cylinder bores 29 with therear shaft hole 12A. One ends of the introducingpassages 51 are opened to the rear cylinder bores 29, respectively, and the other ends of the introducingpassages 51 are opened to therear shaft hole 12A at the sealing circumferential surface. Arear supply passage 22B is formed on the circumferential surface of the rear end of therotary shaft 22. One end of therear supply passage 22B is opened to acylinder suction chamber 19 formed in therear cylinder head 14 and the other end of therear supply passage 22B is communicable with the other end of the introducingpassages 51. In accordance with the rotation of therotary shaft 22, the position of therear supply passage 22B is changed to mechanically switch communication paths between the introducingpassages 51 and therear supply passage 22B. Therefore, a portion of therotary shaft 22 surrounded by the sealing circumferential surface is a rear rotary valve RR which is integrally formed with therotary shaft 22. Thecylinder suction chamber 19 serves as the suction chamber of the present invention. - The following will describe a muffler structure in the
compressor 10. As shown inFIGS. 2 , 3, and 5, thefront space 28B is recessed on thefront cylinder head 13 so as to annularly surround therotary shaft 22. First through thirdfront partition walls 32A through 32C are provided in thefront cylinder head 13 for dividing thefront space 28B into the first through the third front head-side discharge chambers 33A through 33C. The first through the thirdfront partition walls 32A through 32C extend from the bottom surface of thefront cylinder head 13 toward the front block-side discharge chambers 40. The firstfront partition wall 32A is provided at a position adjacent to the front block-side discharge chamber 40, which communicates with thedischarge passage 45, in the rotating direction of therotary shaft 22. - The first and the second
front partition walls rotary shaft 22. Thefront space 28B includes the first front head-side discharge chamber 33A which is formed by the first and the secondfront partition walls side discharge chamber 33A communicates with one front cylinder bore 28 (thefront compression chamber 28A) through onefront discharge port 15A. - The second and the third
front partition walls rotary shaft 22. Thefront space 28B includes the second front head-side discharge chamber 33B formed by the second and the thirdfront partition walls side discharge chamber 33B communicates with one front cylinder bore 28 (thefront compression chamber 28A), which is different from the front cylinder bore 28 communicating with the first front head-side discharge chamber 33A, through onefront discharge port 15A. Thefront space 28B includes the third front head-side discharge chamber 33C formed by the first and the thirdfront partition walls side discharge chamber 33C communicates with the remaining one front cylinder bore 28 (thefront compression chamber 28A) through onefront discharge port 15A. The third front head-side discharge chamber 33C communicates with thedischarge passage 45 through the front block-side discharge chamber 40. - As shown in
FIGS. 2 and 7 , arear space 29B is recessed on therear cylinder head 14 so as to annularly surround therotary shaft 22. First through thirdrear partition walls 34A through 34C are provided in therear cylinder head 14 for dividing therear space 29B into three spaces. The first through the thirdrear partition walls 34A through 34C extend from the bottom surface of therear cylinder head 14 toward the rear block-side discharge chamber 42. The firstrear partition wall 34A is provided at a position adjacent to the rear block-side discharge chamber 42, which communicates with thedischarge passage 45, in the rotating direction of therotary shaft 22. - The first and the second
rear partition walls rotary shaft 22. Therear space 29B includes the first rear head-side discharge chamber 35A formed by the first and the secondrear partition walls side discharge chamber 35A communicates with one rear cylinder bore 29 (therear compression chamber 29A) through onerear discharge port 16A. - The second and the third
rear partition walls rotary shaft 22. Therear space 29B includes the second rear head-side discharge chamber 35B formed by the second and the thirdrear partition walls side discharge chamber 35B communicates with one rear cylinder bore 29 (therear compression chamber 29A) which is different from the rear cylinder bore 29 communicating with the first rear head-side discharge chamber 35A through onerear discharge port 16A. Therear space 29B further includes the third rear head-side discharge chamber 35C formed by the first and the thirdrear partition walls side discharge chamber 35C communicates with the remaining one rear cylinder bore 29 (therear compression chamber 29A) through onerear discharge port 16A. The third rear head-side discharge chamber 35C communicates with thedischarge passage 45 through the rear block-side discharge chamber 42. - As shown in
FIGS. 3 and 7 , two pairs of first front throttles 15F are formed in the gasket G of the frontvalve plate assembly 15 so as to interpose the secondfront partition wall 32B and the thirdfront partition wall 32C, respectively. Two pairs of first rear throttles 16F are formed in the gasket G of the rearvalve plate assembly 16 so as to interpose the second and the thirdrear partition walls front valve plate 20 for communicating with the first front throttles 15F, respectively. Two pairs of second rear throttles 21A are formed in therear valve plate 21 for communicating with the first rear throttles 16F, respectively. Pairs of the first front throttles 15F and the second front throttles 20A which interpose the secondfront partition wall 32B communicate with one front block-side discharge chamber 40. Pairs of the first rear throttles 16F and the second rear throttles 21A which interpose the secondrear partition wall 34B communicate with one rear block-side discharge chamber 42. Pairs of the first front throttles 15F and the second front throttles 20A which interpose the thirdfront partition wall 32C communicate with the other front block-side discharge chamber 40. Pairs of the first rear throttles 16F and the second rear throttles 21A which interpose the thirdrear partition wall 34C communicate with the other rear block-side discharge chamber 42. The first and the second front head-side discharge chambers side discharge chamber 40 with the pairs of first and second front throttles 15F and 20A which interpose the secondfront partition wall 32B. The first and the second rear head-side discharge chambers side discharge chamber 42 with the pairs of first and the second rear throttles 16F and 21A which interpose the secondrear partition wall 34B. The second and the third front head-side discharge chambers side discharge chamber 40 with the pairs of the first and the second front throttles 15F and 20A which interpose the thirdfront partition wall 32C. The second and the third rear head-side discharge chambers side discharge chamber 42 with the pairs of the first and the second rear throttles 16F and 21A which interpose the thirdrear partition wall 34C. The first and the third front head-side discharge chambers front partition wall 32A and do not communicate with each other. The first and the third rear head-side discharge chambers rear partition wall 34A and do not communicate with each other. In thefront space 28B, refrigerant gas flows in the rotating direction of therotary shaft 22 from the first front head-side discharge chamber 33A to the second front head-side discharge chamber 33B and then to the third front head-side discharge chamber 33C, as indicated by the arrows Y inFIG. 3 . In therear space 29B, refrigerant gas flows in the rotating direction of therotary shaft 22 from the first rear head-side discharge chamber 35A to the second rear head-side discharge chamber 35B and then to the third rear head-side discharge chamber 35C, as indicated by the arrows Y inFIG. 7 . The firstfront throttle 15F and the firstrear throttle 16F serve as a first throttle of the present invention. The secondfront throttle 20A and the secondrear throttle 21A serve as a second throttle of the present invention. - The following will describe the operation of the
compressor 10 as constructed above. The refrigerant gas is flowed into thesuction passage 43 through theinlet 44 and supplied to the front and therear suction chambers communication passage 50A and the introducingpassage 50B adjacent to thecommunication passage 50A communicate with each other through thefront groove 22A of the front rotary valve RF. Then, the refrigerant gas is flowed into the front cylinder bores 28 from thefront suction chamber 17 through the front rotary valve RF. - In accordance with the rotation of the
rotary shaft 22, thefront groove 22A is disconnected from thecommunication passage 50A, the communication of thecommunication passage 50A and the introducingpassage 50B is blocked, and the front cylinder bores 28 are shut off. Thus, the front cylinder bores 28 shift to a compression stroke and a discharge stroke. - Referring to
FIG. 6 , on the front side of thecompressor 10, the refrigerant gas discharged to the first front head-side discharge chamber 33A passes through one secondfront throttle 20A and one firstfront throttle 15F formed across the secondfront partition wall 32B along the axial direction of therotary shaft 22 and flows into the front block-side discharge chamber 40. Then, the refrigerant gas passes through the other firstfront throttle 15F and the other secondfront throttle 20A along the axial direction of therotary shaft 22 and flows to the second front head-side discharge chamber 33B different from the first front head-side discharge chamber 33A. - The refrigerant gas discharged from the
front compression chamber 28A facing the second front head-side discharge chamber 33B passes through one pair of the secondfront throttle 20A and the firstfront throttle 15F formed across the thirdfront partition wall 32C in the axial direction of therotary shaft 22 and flows into the front block-side discharge chamber 40 together with the refrigerant gas flowed from the first front head-side discharge chamber 33A. Then, the refrigerant gas passes through the other firstfront throttle 15F and the other secondfront throttle 20A from the front block-side discharge chamber 40 in the axial direction of therotary shaft 22 and flows to the third front head-side discharge chamber 33C different from the second front head-side discharge chamber 33B. - The refrigerant gas discharged from the
front compression chamber 28A facing the third front head-side discharge chamber 33C into the third front head-side discharge chamber 33C is flowed into the front block-side discharge chamber 40 and, then, flowed out to the external refrigerant circuit through thedischarge passage 45 and theoutlet 46 together with the refrigerant gas flowed from the second front head-side discharge chamber 33B. - On the rear side of the
compressor 10, in a state in which refrigerant gas is supplied to thecylinder suction chamber 19, when the rear cylinder bores 29 shift to the suction stroke, therear supply passage 22B communicating with thecylinder suction chamber 19 in the rear rotary valve RR communicates with one introducingpassage 51. Then, the refrigerant gas is supplied to the introducingpassage 51 from thecylinder suction chamber 19 through the rear rotary valve RR and flowed into the rear cylinder bore 29 communicating with the introducingpassage 51. - In accordance with the rotation of the
rotary shaft 22, therear supply passage 22B is disconnected from the introducingpassage 51, the communication between the introducingpassage 51 and thecylinder suction chamber 19 is blocked, and the rear cylinder bores 29 is shut off. Thus, the rear cylinder bores 29 shift to the compression stroke and the discharge stroke. - Referring to
FIG. 7 , on the rear side of thecompressor 10, the refrigerant gas discharged to the first rear head-side discharge chamber 35A passes through one secondrear throttle 21A and one firstrear throttle 16F formed across the secondrear partition wall 34B in the axial direction of therotary shaft 22 and is flowed into the rear block-side discharge chamber 42. Then, the refrigerant gas in the rear block-side discharge chamber 42 passes the other firstrear throttle 16F and the other secondrear throttle 21A in the axial direction of therotary shaft 22 and flows into the second rear head-side discharge chamber 35B different from the first rear head-side discharge chamber 35A. - The refrigerant gas discharged from the
rear compression chamber 29A facing the second rear head-side discharge chamber 35B passes through one secondrear throttle 21A and one firstrear throttle 16F formed across the thirdrear partition wall 34C in the axial direction of therotary shaft 22 and flows into the rear block-side discharge chamber 42 together with the refrigerant gas flowing from the first rear head-side discharge chamber 35A. Then, the refrigerant gas in the rear block-side discharge chamber 42 passes through the other firstrear throttle 16F and the other secondrear throttle 21A in the axial direction of therotary shaft 22 and flows into the third rear head-side discharge chamber 35C which is different from the second rear head-side discharge chamber 35B. The refrigerant gas discharged to the third rear head-side discharge chamber 35C flows into the rear block-side discharge chamber 42, flows through thedischarge passage 45, and is discharged from theoutlet 46 together with the refrigerant gas flowing from the second rear head-side discharge chamber 35B. - Therefore, on the front and the rear sides of the
compressor 10, the refrigerant gas discharged from the front and therear compression chambers side discharge chambers 33A through 33C and the first through the third rear head-side discharge chambers 35A through 35C and the front and the rear block-side discharge chambers outlet 46. Since the refrigerant gas has viscosity, energy is reduced by moving the refrigerant gas along the inner surfaces of the first through the third front head-side discharge chambers 33A through 33C and the first through the third rear head-side discharge chambers 35A through 35C and the inner surfaces of the front and the rear block-side discharge chambers - According to the preferred embodiment of the present invention, the following advantageous effects are obtained.
- (1) On the front side of the
compressor 10, the front block-side discharge chambers 40 may be communicable with the different two of the front head-side discharge chambers 33A through 33C and, on the rear side of thecompressor 10, the rear block-side discharge chambers 42 may be communicable with the different two of the thirst through the third rear head-side discharge chambers 35A through 35C. Therefore, the refrigerant gas may be reciprocated in the discharge path through which the discharged refrigerant gas is flowed to theoutlet 46. As a result, the refrigerant gas may be made to meander. Accordingly, the distance of the flow of the discharged refrigerant gas to theoutlet 46 may be increased to reduce pulsation. Therefore, in order to reduce pulsation, a muffler chamber that projects from the housing H may not need to be provided. Moreover, pulsation may be reduced in a limited volume without providing the muffler chamber. - (2) The
outlet 46 is formed in thefront cylinder block 11. Therefore, the refrigerant gas flowed from the front and therear compression chambers outlet 46 and, then, the refrigerant gas collides against the front and the rear head-side discharge chambers 33A through 33C and 35A through 35C, flows into the front and the rear block-side discharge chambers outlet 46. Therefore, the compressed refrigerant gas may be reciprocated at least once until the refrigerant gas reaches theoutlet 46. - (3) In the front and the
rear cylinder heads rear spaces rotary shaft 22. Therefore, while the refrigerant gas flows in the rotating direction of therotary shaft 22, the refrigerant gas flowing into the front and therear spaces outlet 46. Accordingly, a distance that the discharged refrigerant gas flows to theoutlet 46 may be increased to reduce pulsation. - (4) In the front and the
rear cylinder heads rear spaces rotary shaft 22. Accordingly, the front and therear spaces side discharge chambers 33A through 33C and the first through the third rear head-side discharge chambers 35A through 35C by the first through the thirdfront partition walls 32A through 32C and the first through the thirdrear partition walls 34A through 34C. Further, the front and therear spaces rear cylinder heads rotary shaft 22. Since the annular front and the annularrear spaces front partition walls 32A through 32C and the first through the thirdrear partition walls 34A through 34C, the volume of the first through the third front head-side discharge chambers 33A through 33C and the first through the third rear head-side discharge chambers 35A through 35C may be increased as much as possible to effectively reduce pulsation. - (5) The plurality of the front and the rear block-
side discharge chambers rotary shaft 22. Therefore, the refrigerant gas may be made to be flowed into the plurality of the front and the rear block-side discharge chambers side discharge chambers 33A through 33C and the first through the third rear head-side discharge chambers 35A through 35C and reciprocated therethrough for a plurality of times. Accordingly, a long distance that the discharged gas flows to theoutlet 46 may be secured to reduce pulsation. - (6) The
outlet 46 communicates with one of the three front block-side discharge chambers 40 and one of the three rear block-side discharge chambers 42. Therefore, the refrigerant gas flowed into the front block-side discharge chambers 40 from the first through the third front head-side discharge chambers 33A through 33C may be prevented from directly flowing out through theoutlet 46 from the front block-side discharge chambers 40. Similarly, the refrigerant gas flowed into the front and the rear block-side discharge chambers 42 from the first through the third rear head-side discharge chambers 35A through 35C may be prevented from directly flowing out through theoutlet 46 from the rear block-side discharge chambers 42. As a result, a distance that the discharged refrigerant gas flows to theoutlet 46 may be secured to reduce pulsation. - (7) The front and the rear block-
side discharge chambers rotary shaft 22. Therefore, the gaps of the front and the rear cylinder bores 28 and 29 adjacent to one another are effectively used for the front and the rear block-side discharge chambers compressor 10 in the axial direction may be suppressed. - (8) The first front throttles 15F and the first rear throttles 16F are provided in the gaskets G of the front and the rear
valve plate assemblies rear valve plates side discharge chambers 33A through 33C and the first through the third rear head-side discharge chambers 35A through 35C with the front and the rear block-side discharge chambers side discharge chambers 33A through 33C and the first through the third rear head-side discharge chambers 35A through 35C and the front and the rear block-side discharge chambers - The above preferred embodiment may be modified into various alternative embodiments, as exemplified below. The diameter of the first front throttles 15F and the first rear throttles 16F and the second front throttles 20A and the second rear throttles 21A may be changed.
- The front and the
rear discharge ports valve plate assemblies - Only the gaskets G may be provided between the front and the
rear cylinder blocks rear cylinder heads rear discharge ports - The front and the rear block-
side discharge chambers side discharge chambers - Four or more partition walls may be provided in each of the front and the
rear cylinder heads side discharge chambers 40 and four or more rear block-side discharge chambers 42 may be provided to increase the number of times of the reciprocation of the refrigerant gas. On the other hand, two partition walls may be provided in each of the front and therear cylinder heads side discharge chambers 40 and two or more rear block-side discharge chambers 42 may be provided to reduce the number of times of reciprocation of the refrigerant gas. - According to the preferred embodiment, the
outlet 46 is opened through thefront cylinder block 11. Alternatively, an outlet may be formed to be opened through therear cylinder block 12, or the front and therear cylinder heads - According to the preferred embodiment, the rotary valves are adapted to suctioning on the front and the rear sides of the
compressor 10. Alternatively, suction valves may be adapted to suctioning on the front and the rear sides in stead of the rotary valves. - According to the preferred embodiment, on the rear side of the
compressor 10, the refrigerant gas in thefront suction chambers 18 is collected in thecylinder suction chamber 19 and is flowed into the rear cylinder bores 29 from thecylinder suction chamber 19 through the rear rotary valve RR. Alternatively, on the rear side of thecompressor 10, as in the front side, therear suction chambers 18 and therear shaft hole 12A may communicate through communication passages and introducing grooves, therear shaft hole 12A and the rear cylinder bores 29 may separately communicate through introducing passages, respectively. Thus, the refrigerant gas may be flowed into the rear cylinder bores 29 from therear suction chambers 18 through the communication passages, the introducing grooves of the rear rotary valve RR and the introducing passages. - According to the preferred embodiment, the refrigerant gas passed through the
inlet 44 is supplied to the front and therear compression chambers front groove 22A and therear supply passage 22B formed on the surface of therotary shaft 22. Alternatively, a rotary shaft may be formed to include an inner passage therein as a hollow shaft. Thus, after refrigerant gas flowed through theinlet 44 may be guided to the inside of the front and therear cylinder heads rear compression chambers - According to the preferred embodiment, the refrigerant gas flowed through the
inlet 44 is supplied to the front and therear suction chambers suction passage 43 formed in the front and therear cylinder blocks inlet 44 may be supplied to the front and therear suction chambers crank chamber 25. - According to the preferred embodiment, the volume of one
front suction chamber 17 and onerear suction chamber 18 which communicate with thesuction passage 43 is set larger than the volume of the other twofront suction chambers 17 and the other tworear suction chambers 18. Alternatively, the volume of the other twofront suction chambers 17 and the other tworear suction chambers 18 may be set larger than the volume of the front and therear suction chambers suction passage 43. - The three
front suction chambers 17 may have the same volume and also threerear suction chambers 18 may have the same volume. - Only one front block-
side discharge chamber 40 may be provided and eachfront space 28B may be partitioned into two front head-side discharge chambers. Only one rear block-side discharge chamber 42 may be provided and eachrear space 29B may be partitioned into two rear head-side discharge chambers. - The number of the front and the rear cylinder bores 28 and 29 may be changed.
- According to the preferred embodiment, the
compressor 10 is a double-headed piston type swash plate compressor including the double-headedpistons 30. Alternatively, the piston type swash plate compressor may be a single-headed piston type swash plate compressor including a single-headed piston.
Claims (6)
1. A piston type swash plate compressor comprising:
a housing;
a cylinder block formed in the housing;
a cylinder head formed in the housing, the cylinder head connected to an end of the cylinder block;
a rotary shaft rotatably supported by the cylinder block;
a plurality of cylinder bores arranged around the rotary shaft;
a plurality of pistons respectively accommodated in the cylinder bores;
a swash plate integrally rotating with the rotary shaft, the swash plate engaged with the pistons;
a plurality of compression chambers respectively defined in the cylinder bores by the pistons;
a plurality of head-side discharge chambers provided in the cylinder head;
a plurality of block-side discharge chambers provided in the cylinder block;
an outlet formed through the housing, the outlet through which compressed refrigerant gas is flowed outside the housing; and
a discharge path formed in the housing, the discharge path through which refrigerant gas is flowed from the compression chamber to the outlet through the head-side discharge chamber and the block-side discharge chamber,
wherein, after refrigerant gas flowed from the compression chamber is flowed through one head-side discharge chamber which communicates with the compression chamber and one block-side discharge chamber, the refrigerant gas is flowed to another head-side discharge chamber.
2. The piston type swash plate compressor according to claim 1 , wherein a plurality of the head-side discharge chambers is formed by dividing a space formed annularly around the rotary shaft in a rotating direction of the rotary shaft by partition walls.
3. The piston type swash plate compressor according to claim 1 , wherein a plurality of the block-side discharge chambers is formed around the rotary shaft, after refrigerant gas flowed from the compression chamber is flowed through the discharge path from one block-side discharge chamber to one head-side discharge chamber, the refrigerant gas is flowed to another block-side discharge chamber.
4. The piston type swash plate compressor according to claim 3 , wherein each block-side discharge chamber is located between any two adjacent cylinder bores.
5. The piston type swash plate compressor according to claim 1 , wherein a gasket is provided between the cylinder block and the cylinder head, a first throttle is formed through the gasket, at least one of the block-side discharge chambers communicates with at least one of the head-side discharge chambers through the first throttle.
6. The piston type swash plate compressor according to claim 1 , wherein a valve plate is provided between the cylinder block and the cylinder head, a part of the valve plate forms a discharge valve, a second throttle is formed in the valve plate and at least one of the block-side discharge chamber communicates with at least one of the head-side discharge chamber through the second throttle.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2013-066641 | 2013-03-27 | ||
JP2013066641A JP5915576B2 (en) | 2013-03-27 | 2013-03-27 | Piston type swash plate compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
US20140294617A1 true US20140294617A1 (en) | 2014-10-02 |
Family
ID=51596247
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/221,617 Abandoned US20140294617A1 (en) | 2013-03-27 | 2014-03-21 | Piston type swash plate compressor |
Country Status (5)
Country | Link |
---|---|
US (1) | US20140294617A1 (en) |
JP (1) | JP5915576B2 (en) |
KR (1) | KR101534601B1 (en) |
CN (1) | CN104074710A (en) |
BR (1) | BR102014007234A2 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR200487258Y1 (en) | 2017-08-03 | 2018-08-28 | 김태균 | Holder Bar For Crop Duster |
CN110318973B (en) * | 2018-03-30 | 2020-10-23 | 株式会社丰田自动织机 | Piston type compressor |
Citations (6)
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US5051069A (en) * | 1987-05-13 | 1991-09-24 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Multi-cylinder refrigerant gas compressor with a muffling arrangement |
US5674054A (en) * | 1993-05-21 | 1997-10-07 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Reciprocating type compressor |
US6402483B1 (en) * | 1999-06-30 | 2002-06-11 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Double-headed piston compressor |
US20070292280A1 (en) * | 2006-06-15 | 2007-12-20 | Yomg-Wan Choi | Inside and outside structures of discharging refrigerant in bi-directional swash plate type compressor |
US20080286125A1 (en) * | 2007-02-02 | 2008-11-20 | Kabushiki Kaisha Toyota Jidoshokki | Double-headed piston type compressor |
US20090238698A1 (en) * | 2005-09-21 | 2009-09-24 | Sanden Corporation | Reciprocal Compressor |
Family Cites Families (12)
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JP2590662Y2 (en) * | 1993-07-12 | 1999-02-17 | 株式会社豊田自動織機製作所 | Reciprocating compressor |
JP3301570B2 (en) * | 1993-12-27 | 2002-07-15 | 株式会社豊田自動織機 | Reciprocating compressor |
JPH09144651A (en) * | 1995-11-20 | 1997-06-03 | Toyota Autom Loom Works Ltd | Reciprocating compressor |
JP3266504B2 (en) * | 1996-04-19 | 2002-03-18 | 株式会社ゼクセルヴァレオクライメートコントロール | Swash plate compressor |
JPH11173274A (en) * | 1997-12-04 | 1999-06-29 | Zexel:Kk | Variable displacement type swash plate compressor without clutch |
JP3820766B2 (en) * | 1998-03-06 | 2006-09-13 | 株式会社豊田自動織機 | Compressor |
JP2000104660A (en) * | 1998-09-28 | 2000-04-11 | Sanden Corp | Compressor |
JP4692866B2 (en) * | 2001-07-05 | 2011-06-01 | 株式会社ヴァレオサーマルシステムズ | Swash plate compressor |
KR101159863B1 (en) * | 2006-07-24 | 2012-06-25 | 한라공조주식회사 | Compressor |
JP2010013987A (en) * | 2008-07-02 | 2010-01-21 | Toyota Industries Corp | Refrigerant suction structure in piston type compressor |
JP5783354B2 (en) * | 2011-03-07 | 2015-09-24 | サンデンホールディングス株式会社 | Compressor |
WO2012133669A1 (en) * | 2011-03-31 | 2012-10-04 | 株式会社 豊田自動織機 | Swash-plate-type compressor |
-
2013
- 2013-03-27 JP JP2013066641A patent/JP5915576B2/en not_active Expired - Fee Related
-
2014
- 2014-03-21 US US14/221,617 patent/US20140294617A1/en not_active Abandoned
- 2014-03-26 CN CN201410116904.0A patent/CN104074710A/en active Pending
- 2014-03-26 KR KR1020140035050A patent/KR101534601B1/en not_active IP Right Cessation
- 2014-03-26 BR BRBR102014007234-9A patent/BR102014007234A2/en not_active IP Right Cessation
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5051069A (en) * | 1987-05-13 | 1991-09-24 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Multi-cylinder refrigerant gas compressor with a muffling arrangement |
US5674054A (en) * | 1993-05-21 | 1997-10-07 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Reciprocating type compressor |
US6402483B1 (en) * | 1999-06-30 | 2002-06-11 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Double-headed piston compressor |
US20090238698A1 (en) * | 2005-09-21 | 2009-09-24 | Sanden Corporation | Reciprocal Compressor |
US20070292280A1 (en) * | 2006-06-15 | 2007-12-20 | Yomg-Wan Choi | Inside and outside structures of discharging refrigerant in bi-directional swash plate type compressor |
US20080286125A1 (en) * | 2007-02-02 | 2008-11-20 | Kabushiki Kaisha Toyota Jidoshokki | Double-headed piston type compressor |
Also Published As
Publication number | Publication date |
---|---|
KR101534601B1 (en) | 2015-07-24 |
JP2014190238A (en) | 2014-10-06 |
KR20140118845A (en) | 2014-10-08 |
JP5915576B2 (en) | 2016-05-11 |
BR102014007234A2 (en) | 2015-08-04 |
CN104074710A (en) | 2014-10-01 |
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