US20130343922A1 - Swash-plate-type compressor - Google Patents
Swash-plate-type compressor Download PDFInfo
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- US20130343922A1 US20130343922A1 US14/002,801 US201214002801A US2013343922A1 US 20130343922 A1 US20130343922 A1 US 20130343922A1 US 201214002801 A US201214002801 A US 201214002801A US 2013343922 A1 US2013343922 A1 US 2013343922A1
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- Prior art keywords
- suction
- chamber
- swash plate
- suction chamber
- communication
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- 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
- F04B27/0821—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 component parts, details, e.g. valves, sealings, lubrication
- F04B27/0839—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 component parts, details, e.g. valves, sealings, lubrication valve means, e.g. valve plate
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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
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1009—Distribution members
- F04B27/1018—Cylindrical distribution members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
- F04B39/123—Fluid connections
Definitions
- the present invention relates to a swash plate compressor including a cylinder block having a shaft hole into which a rotary shaft is inserted, and a plurality of cylinder bores located around the shaft hole and arranged along a peripheral direction.
- the cylinder bores respectively receive pistons.
- Patent Document 1 describes a double-headed piston type swash plate compressor employing a double-headed piston.
- a swash plate compressor 80 of Patent Document 1 includes a cylinder block 81 having three cylinder bores 81 a.
- a double-headed piston 82 is accommodated in each cylinder bore 81 a.
- the cylinder block 81 includes a single suction chamber 83 , which is arranged between two adjacent cylinder bores 81 a , and a single discharge chamber 84 , which is arranged at a different location between two adjacent cylinder bores 81 a.
- the suction chamber 83 and the discharge chamber 84 each having a necessary volume to suppress pulsation can be arranged in the cylinder block 81 by effectively using the region between adjacent cylinder bores 81 a . This avoids enlargement of the swash plate compressor 80 .
- refrigerant is drawn from the suction chamber into the cylinder bores 81 a when a reed type suction valve opens a suction port.
- the suction valve opens and closes in accordance with the difference in pressure between the interior of the corresponding cylinder bore 81 a and the suction chamber.
- the suction valve does not open until the pressure in the cylinder bore 81 a decreases to a predetermined pressure.
- the suction valve may not open at the desired timing. This may decrease the suction efficiency.
- the use of a rotary valve that mechanically communicates the suction chamber and cylinder bores is effective for the swash plate compressor 80 that avoids enlargement.
- Patent Document 1 Japanese Laid-Open Patent Publication No. H9-317633
- Patent Document 2 Japanese Laid-Open Patent Publication No. 2007-138925
- Patent Document 3 Japanese Laid-Open Patent Publication No. 2007-270790
- a swash plate compressor 90 disclosed in Patent Document 2 that employs a rotary valve
- refrigerant is first sent into an accommodation chamber 93 a (suction chamber) in a front housing 93 through a communication groove 98 from a swash plate chamber 99 .
- the refrigerant in the front housing 93 (accommodation chamber 93 a ) is sent toward a cylinder block 91 though a supply passage 92 a .
- a rotation shaft 92 is must include the supply passage 92 a , which extends from the front housing 93 to the cylinder block 91 . This lengthens the supply passage 92 a in the axial direction.
- the formation of the supply passage 92 a enlarges the swash plate compressor 90 in the axial direction.
- a swash plate compressor 100 of Patent Document 3 that also employs a rotary valve includes a rotation shaft 101 having a supplying passage 102 formed therein and a conducting hole 101 a for communicating inside and outside of the supplying passage 102 .
- a cylinder block 104 includes a suction recess 105 located around the rotation shaft 101 .
- the conducting hole 101 a communicates a swash plate chamber 106 with the supplying passage 102 through the suction recess 105 .
- each of the swash plate chambers 99 and 106 functions as suction chamber. This complicates the structure of the rotary valve 107 and enlarges the rotary valve 107 . This also enlarges the body of the swash plate compressor 90 and 100 .
- one aspect of the present invention is a swash plate compressor including a cylinder block, a swash plate, pistons, a rotation shaft and a rotary valve.
- the cylinder block includes a shaft hole, cylinder bores, a swash plate chamber and a suction chamber.
- the shaft hole extends through the cylinder block.
- the cylinder bores are arranged along a circumferential direction around the shaft hole.
- the suction chamber is arranged in a space between the adjacent cylinder bores and is separated from the swash plate chamber.
- the swash plate is accommodated in the swash plate chamber.
- the pistons are connected with the swash plate and respectively arranged in the cylinder bores.
- the rotation shaft is arranged in the shaft hole and operative to rotate integrally with the swash plate.
- the rotary valve is provided with the rotation shaft to rotate integrally with the rotation shaft.
- the cylinder block includes a suction chamber communication passage that defines a communication path between the suction chamber and the shaft hole, and bore communication passages that define independent communication paths between the cylinder bores and the shaft hole.
- the rotary valve rotates integrally with the rotation shaft to provide sequential communication between the suction chamber communication passage and the bore communication passages.
- the suction chamber and cylinder bores are arranged around the rotary valve along a circumferential direction.
- body size of the rotary valve and the swash plate compressor are prevented from enlarged.
- suction efficiency is prevented from being reduced as compared to when a suction valve is employed.
- the suction chamber includes a plurality of suction chambers.
- Each of the plurality of suction chambers is arranged between a circumferentially adjacent pair of the cylinder bores.
- the suction chamber communication passage includes a plurality of suction chamber communication passages that provide independent communication between the suction chambers and the shaft hole.
- the suction chamber and cylinder bores are alternately arranged around the rotary valve along a circumferential direction.
- the intake passage is simply formed at a portion of the rotary valve to extend in the circumferential direction.
- the cylinder block includes a plurality of discharge chambers.
- Each of the discharge chambers is arranged in a space between adjacent cylinder bores.
- thermally expanded portions are uniformly distributed in the cylinder blocks along the radial direction. This prevents each cylinder bore and each piston from adversely affected by a thermal expansion.
- the discharge chambers are arranged outward in a radial direction of the cylinder block from the suction chambers.
- the cylinder block includes a suction port to which an external pipe is connected, and a suction passage that provides communication between the suction port and the suction chamber.
- the suction passage is separated from the swash plate chamber.
- the rotation shaft having a rotary valve receives heat generated by sliding friction due to the rotation of the rotation shaft.
- heat exchange between the refrigerant and the rotation shaft is only carried out when the refrigerant passes through the rotary valve.
- an axial length of the rotary valve is shortened so that the refrigerant is sufficiently prevented from being heated. This improves the suction efficiency.
- the suction chamber communication passage is a recess formed in an inner wall of the shaft hole.
- the recess includes an open end in communication with the swash plate chamber.
- a thrust bearing is arranged between the swash plate and the open end of the recess. The thrust bearing closes the open end of the recess.
- the suction chamber communication passage is formed together with when the cylinder block is molded. This reduces time for manufacturing the cylinder block as compared with the case in which the cylinder block is molded and then the cylinder block is subjected to a cutting work by a drill or the like to form the suction chamber communication passage.
- the suction chamber communication passage includes a first recess and a second recess.
- the first recess is formed in an inner wall of the suction chamber.
- the first recess includes an open end, which opens toward an end face of the cylinder block in an axial direction.
- the second recess is formed in an inner wall of the shaft hole.
- the second recess includes an open end in communication with the swash plate chamber.
- a thrust bearing is arranged between the swash plate and the open end of the second recess. The thrust bearing closes the open end of the second recess.
- the suction chamber communication passage is formed together with when the cylinder block is molded.
- the size of an opening between the suction chamber communication passage and the swash plate chamber is reduced so that the size of the thrust bearing serving as a closing member can be reduced.
- the cylinder bores are three cylinder bores.
- the present invention provides a swash plate compressor, which is decreased in size while suppresses pulsation and suction efficiency from being lowered.
- FIG. 1 is a cross-sectional view showing a double-headed piston type swash plate compressor according to a first embodiment of the present invention taken along line 1 - 1 in FIG. 3 .
- FIG. 2 is a cross-sectional view showing the double-headed piston type swash plate compressor according to the first embodiment taken along line 2 - 2 in FIG. 3 .
- FIG. 3 is a cross-sectional view showing a front discharge chamber and a front suction chamber taken along line 3 - 3 in FIG. 1 .
- FIG. 4 is a cross-sectional view taken along line 4 - 4 of FIG. 1 showing a front cylinder bore, the front suction chamber and the front discharge chamber.
- FIG. 5 is a partial cross-sectional view showing a double-headed piston type swash plate compressor according to a second embodiment of the present invention.
- FIG. 6 is a development view showing a rotary valve and inside of a shaft hole of FIG. 5 .
- FIG. 7( a ) is a cross-sectional view taken along line 7 a - 7 a of FIG. 5 showing a cylinder block as viewed from a front suction chamber.
- FIG. 7( b ) is a cross-sectional view taken along line 7 b - 7 b of FIG. 5 showing a cylinder block as viewed from a shaft hole.
- FIG. 8 is a partial cross-sectional view showing a double-headed piston type swash plate compressor of another example.
- FIG. 9 is a cross-sectional view showing a double-headed piston type swash plate compressor of another example.
- FIG. 10 is a development view showing a front rotary valve of another example.
- FIG. 11 is a diagram showing a Patent Document 1.
- FIG. 12 is a diagram showing a Patent Document 2.
- FIG. 13 is a diagram showing a Patent Document 3.
- a first embodiment of the present invention that embodies a swash plate compressor in a double-headed piston type swash plate compressor 10 will now be described with reference to FIGS. 1 to 4 .
- a double-headed piston type swash plate compressor 10 (hereinafter simply referred to as the compressor 10 ) includes a housing H.
- a cylinder block 11 which is located at a front side (left side as viewed in FIG. 1 ), is coupled to a front housing 13 with a front valve/port formation body 15 arranged in between.
- a cylinder block 12 which is located at a rear side (right side as viewed in FIG. 1 ), is coupled to a rear housing 14 with a rear valve/port formation body 16 arranged in between.
- the housing H is formed by the two cylinder blocks 11 and 12 and the front and rear housings 13 and 14 sandwiching the cylinder blocks 11 and 12 .
- a rotation shaft 22 is inserted into shaft holes 11 a and 12 a that are respectively formed in the cylinder blocks 11 and 12 .
- the rotation shaft 22 is supported to be rotatable by sealing surfaces defined on the wall surfaces of the shaft holes 11 a and 12 a .
- the rotation shaft 22 is inserted through insertion holes 15 d and 16 d respectively formed in the centers of the front valve/port formation body 15 and the rear valve/port formation body 16 .
- a lip type shaft seal 23 hermetically seals the space between the front housing 13 and the rotation shaft 22 .
- the shaft seal 23 is accommodated in an accommodation chamber 13 c defined between the inner wall surface of the front housing 13 and the circumferential surface of the rotation shaft 22 .
- a swash plate 24 which rotates integrally with the rotation shaft 22 , is fixed to the rotation shaft 22 .
- the swash plate 24 is arranged in the cylinder block 11 , 12 and accommodated in a swash plate chamber 25 , which is formed between the cylinder blocks 11 and 12 .
- a thrust bearing 26 is arranged between the front cylinder block 11 and an annular base 24 a of the swash plate 24 .
- a thrust bearing 27 is arranged between the rear cylinder block 12 and the base 24 a of the swash plate 24 .
- the rotation shaft 22 has an axis L.
- the thrust bearings 26 and 27 sandwich the swash plate 24 to restrict movement of the swash plate 24 along the axial direction.
- the thrust bearings 26 and 27 are pushed respectively toward open ends of the shaft holes 11 a and 12 a in the cylinder blocks 11 and 12 .
- three front cylinder bores 28 are arranged around the rotation shaft 22 in the front cylinder block 11 .
- three rear cylinder bores 29 are arranged around the rotation shaft 22 in the rear cylinder block 12 .
- Each front cylinder bore 28 is paired with one of the rear cylinder bores 29 .
- the front and rear cylinder bores 28 and 29 in each pair are aligned with each other in the axial direction (front to rear direction) in which the axis L extends.
- a double-headed piston 30 serving as a piston is inserted in each pair of the cylinder bore 28 and 29 .
- the front cylinder bore 28 is closed by the front valve/port formation body 15 and the corresponding double-headed piston 30
- the rear cylinder bore 29 is closed by the rear valve/port formation body 16 and the corresponding double-headed piston 30 .
- a front compression chamber 28 a is defined in the front cylinder bore 28 by the double-headed piston 30 and the front valve/port formation body 15
- a rear compression chamber 29 a is defined in the rear cylinder bore 29 by the double-headed piston 30 and the rear valve/port formation body 16 .
- the front housing 13 and cylinder block 11 include three front suction chambers 17 , which surround the rotation shaft 22 and extend through the front valve/port formation body 15 in. As shown in FIG. 4 , each of the three front suction chambers 17 are arranged between the front cylinder bores 28 that are circumferentially adjacent around the shaft hole 11 a. The three front suction chambers 17 are arranged at equal interval at the outer side of the shaft hole 11 a.
- one of the three front suction chambers 17 has a longer length in the axial direction of the rotation shaft 22 and a greater volume than the other two front suction chambers 17 .
- each of the three front suction chambers 17 is in communication with the accommodation chamber 13 c of the front housing 13 .
- the three front suction chambers 17 are in communication with one another about the accommodation chamber 13 c . This forms a single continuous space.
- a front discharge chamber 28 b is defined around the rotation shaft 22 between the front housing 13 and the front valve/port formation body 15 .
- the front discharge chamber 28 b is a region into which the refrigerant from the three front compression chambers 28 a is discharged. Further, the front discharge chamber 28 b is annular and defined in the peripheral portion of the front housing 13 .
- each portion facing one of the front compression chambers 28 a through the front valve/port formation body 15 forms an opening.
- the portions facing the front compression chambers 28 a are in communication with one another through passages. This forms a single continuous space.
- three front discharge chambers 40 which are in communication with the front discharge chamber 28 b, are defined in the cylinder block 11 .
- the front discharge chambers 40 extend from the front cylinder block 11 and through the front valve/port formation body 15 .
- the three front discharge chambers 40 are arranged around the rotation shaft 22 .
- Each front discharge chamber 40 is formed between the front cylinder bores 28 that are adjacent in the circumferential direction of the shaft hole 11 a . Further, the front discharge chambers 40 are located outward in the radial direction of the cylinder block 11 from the front suction chambers 17 .
- the front valve/port formation body 15 includes discharge ports 15 a , which are arranged in correspondence with the front cylinder bores 28 , and discharge valves 15 b , which are arranged in correspondence with the discharge ports 15 a . Further, the front valve/port formation body 15 includes retainers 15 c , which restrict the open amount of the corresponding discharge valves 15 b.
- each of the three rear suction chambers 18 is arranged in a space between the rear cylinder bores 29 that are adjacent in the circumferential direction of the shaft hole 12 a .
- One of the three rear suction chambers 18 has a longer length in the axial direction of the rotation shaft 22 and a greater volume than the other two rear suction chambers 18 .
- a rear housing suction chamber 19 is defined between a central part of the rear housing 14 and the rear valve/port formation body 16 .
- the three rear suction chambers 18 are in communication with one another in the rear housing suction chamber 19 .
- the three rear suction chambers 18 are in continuous communication with one another about the rear housing suction chamber 19 .
- Each front suction chamber 17 is paired with one of the rear suction chambers 18 .
- the front suction chamber 17 and rear suction chamber 18 in each pair are aligned in the front to rear direction in which the axis L extends.
- the front suction chamber 17 and rear suction chamber 18 are formed at opposite sides of the swash plate 24 in the cylinder blocks 11 and 12 .
- An annular rear discharge chamber 29 b is defined around the rotation shaft 22 between the rear housing 14 and the rear valve/port formation body 16 .
- the rear discharge chamber 29 b is a region into which the refrigerant from the three rear compression chambers 29 a is discharged. Further, the rear discharge chamber 29 b is defined at the outer side of the rear housing suction chamber 19 .
- each portion facing one of the rear cylinder bores 29 through the rear valve/port formation body 16 forms an opening having a size that conforms to the circular rear compression chamber 29 a.
- the portions facing the rear cylinder bores 29 are in communication with one another through passages. This forms a single continuous space.
- the cylinder block 12 includes three rear discharge chamber 42 , which are in communication with the rear discharge chamber 29 b.
- the rear discharge chambers 42 extend from the rear housing 14 through the rear valve/port formation body 16 and to the rear cylinder block 12 .
- the three rear discharge chambers 42 are arranged around the shaft hole 12 a and formed between the rear cylinder bores 29 that are adjacent in the circumferential direction of the shaft hole 12 a .
- the rear discharge chambers 42 are formed outward in the radial direction of the cylinder block 12 from the rear suction chambers 18 .
- Each front discharge chamber 28 b is paired with one of the rear discharge chambers 29 b.
- the front discharge chamber 28 b and rear discharge chamber 29 b in each pair are aligned in the front to rear direction in which the axis L extends.
- the rear valve/port formation body 16 includes discharge ports 16 a , which are arranged in correspondence with the rear discharge chambers 29 b, and discharge valves 16 b, which are arranged in correspondence with the discharge ports 16 a . Further, the rear valve/port formation body 16 includes retainers 16 c, which restrict the open amount of the discharge valves 16 b.
- a suction passage 43 is formed in the cylinder blocks 11 and 12 .
- the suction passage 43 has a front opening, which is in communication with the front suction chamber 17 having the largest volume, and a rear opening, which is in communication with the rear suction chamber 18 having the largest volume.
- a suction port 44 is formed in the front cylinder block 11 .
- the suction port 44 has one end that opens in the outer surface of the cylinder block 11 and another end that opens in the wall surface of the suction passage 43 .
- An external pipe 32 of an external refrigerant circuit that is arranged outside the compressor 10 is connected to one open end of the suction port 44 .
- the suction passage 43 is formed in the cylinder blocks 11 and 12 and separated from the swash plate chamber 25 .
- the suction passage 43 is formed in communication with the front and rear suction chambers 17 and 18 having the largest volume. Thus, the suction passage 43 is sandwiched in the axial direction by the front discharge chamber 40 and the rear discharge chamber 42 , which are located at the outer sides of the suction chambers 17 and 18 .
- a discharge passage 45 is formed in the cylinder blocks 11 and 12 .
- the discharge passage 45 has a front opening, which is in communication with one of the three front discharge chambers 40 , and a rear opening, which is in communication with one of the three rear discharge chambers 42 .
- a discharge port 46 is formed in the cylinder block 11 .
- the discharge port 46 has one end that opens in the outer surface of the cylinder block 11 and another end that opens in the wall surface of the discharge passage 45 .
- the external pipe 33 of the external refrigerant circuit that is arranged outside the compressor 10 , is connected to the discharge port 46 .
- the discharge passage 45 is separated in the circumferential direction of the cylinder blocks 11 and 12 from the suction passage 43 . More specifically, the front discharge chamber 40 and rear discharge chamber 42 sandwiching the discharge passage 45 in the axial direction is separated in the circumferential direction from the front discharge chamber 40 and rear discharge chamber 42 sandwiching the suction passage 43 in the axial direction.
- the external refrigerant circuit When forming a refrigerating cycle for a vehicle air conditioner with the compressor 10 , the external refrigerant circuit connects the discharge port 46 and the suction port 44 of the compressor 10 via the external pipes 32 and 33 .
- the external refrigerant circuit includes a condenser, an expansion valve, and an evaporator, which are arranged in order from the discharge port 46 of the compressor 10 in the external refrigerant circuit.
- suction chamber communication passages 50 a communicating the front suction chambers 17 and the shaft hole 11 a are formed in the cylinder block 11 .
- Each suction chamber communication passage 50 a has one end that opens in the corresponding front suction chamber 17 and another end that opens in the sealing surface of the wall defining the shaft hole 11 a.
- the suction chamber communication passages 50 a formed in the cylinder block 11 extend slightly inclined relative to the radial direction of the cylinder block 11 .
- Front bore communication passages 50 b communicating the shaft hole 11 a and the front cylinder bores 28 are formed in the cylinder block 11 .
- Each front bore communication passage 50 b has one end that opens in the sealing surface of the wall defining the shaft hole 11 a and another end that opens in the corresponding front cylinder bore 28 .
- the suction chamber communication passages 50 a and front bore communication passages 50 b are alternately arranged in the circumferential direction of the shaft hole 11 a.
- an intake groove 22 a is formed in the circumferential surface of the front side of the rotation shaft 22 .
- the intake groove 22 a is recessed in the circumferential surface of the rotation shaft 22 , which is a solid shaft, at the side closer to the front housing 13 .
- the intake groove 22 a opens towards the sealing surface of the wall defining the shaft hole 11 a and is independently communicable with the suction chamber communication passages 50 a and the front bore communication passages 50 b.
- Rotation of the rotation shaft 22 changes the position of the intake groove 22 a . This mechanically switches the suction chamber communication passages 50 a and front bore communication passages 50 b that come into communication with the intake groove 22 a.
- the portion of the rotation shaft 22 surrounded by the sealing surface forms a front rotary valve RF, which is formed integrally with the rotation shaft 22 .
- the intake groove 22 a communicates one of the suction chamber communication passage 50 a and the front bore communication passage 50 b that is adjacent in the circumferential direction of the shaft hole 11 a.
- the suction chamber communication passage 50 a and front bore communication passage 50 b that are independently in communication through the intake groove 22 a draw in refrigerant from the corresponding front suction chamber 17 to the adjacent front cylinder bore 28 .
- the intake groove 22 a serves as a supplying passage, which communicates the front cylinder bore 28 and the front suction chamber 17 in the front rotary valve RF.
- rear intake passages 51 communicating the rear cylinder bores 29 and the shaft hole 12 a are formed in the cylinder block 12 .
- Each rear intake passage 51 has one end that opens in the corresponding rear cylinder bore 29 and another end that opens in the sealing surface of the wall defining the shaft hole 12 a .
- a supply passage 22 b is formed in the circumferential surface of the rear side of the rotation shaft 22 .
- the supply passage 22 b has one end that opens in the rear housing suction chamber 19 of the rear housing 14 and another end that is communicable with the rear intake passages 51 .
- Rotation of the rotation shaft 22 changes the position of the supply passage 22 b . This mechanically switches the rear intake passages 51 that come into communication with the supply passage 22 b .
- the portion of the rotation shaft 22 surrounded by the sealing surface forms a rear rotary valve RR, which is formed integrally with the rotation shaft 22 .
- Refrigerant is drawn through the suction port 44 into the suction passage 43 and supplied to each front suction chamber 17 and each rear suction chamber 18 .
- each front cylinder bore 28 performs the intake stroke, one of the suction chamber communication passages 50 a and the adjacent front bore communication passage 50 b come into communication through the intake groove 22 a of the front rotary valve RF, as shown in FIG. 4 .
- the refrigerant is then drawn from the front suction chamber 17 through the front rotary valve RF into the corresponding front cylinder bore 28 .
- the intake groove 22 a goes out of communication with the suction chamber communication passage 50 a.
- the suction chamber communication passage 50 a and the front bore communication passage 50 b are not in communication with each other, and the front cylinder bore 28 is closed.
- the front cylinder bore 28 performs the compression stroke and discharge stroke.
- the refrigerant in the front compression chamber 28 a is forced through the discharge valve 15 b from the discharge port 15 a and discharged to the front discharge chamber 28 b.
- the refrigerant discharged to the front discharge chamber 28 b flows out of the front discharge chamber 40 through the discharge passage 45 and the discharge port 46 and into the external refrigerant circuit.
- each rear cylinder bore 29 performs the intake stroke in a state in which refrigerant is supplied to the rear housing suction chamber 19
- the supply passage 22 b which is in communication with the rear housing suction chamber 19 in the rear rotary valve RR, comes into communication with one or two rear intake passage 51 .
- the supply passage 22 b goes out of communication with the rear intake passage 51 .
- the rear intake passage 51 and the rear housing suction chamber 19 are not in communication with each other, and the rear cylinder bore 29 is closed.
- the rear cylinder bore 29 performs the compression stroke and the discharge stroke.
- the refrigerant in the rear compression chamber 29 a is forced through the discharge valve 16 b from the discharge port 16 a and discharged to the rear discharge chamber 29 b.
- the refrigerant discharged to the rear discharge chamber 29 b flows out of the rear discharge chamber 42 through the discharge passage 45 and the discharge port 46 and into the external refrigerant circuit.
- the present embodiment has the advantages described below.
- the three front cylinder bores 28 are formed around the shaft hole 11 a of the cylinder block 11 , and each front suction chamber 17 is arranged between the front cylinder bores 28 that are adjacent to each other. That is, the front cylinder bores 28 and the front suction chambers 17 are alternately arranged around the shaft hole 11 a.
- the suction chamber communication passages 50 a which communicates front suction chambers 17 with the shaft hole 11 a
- the front bore communication passages 50 b which communicates the front cylinder bores 28 with the shaft hole 11 a
- the suction chamber communication passages 50 a and the front bore communication passages 50 b are alternately arranged in the circumferential direction of the shaft hole 11 a.
- the refrigerant in each front suction chamber 17 is directly drawn into the intake groove 22 a through the corresponding suction chamber communication passage 50 a, and then drawn in the front cylinder bore 28 through the front bore communication passage 50 b.
- the intake groove 22 a is simply formed at a portion of the rotary valve RF to extend in the circumferential direction. This simplifies the shape of the front rotary valve RF and therefore shortens an axial length of the front rotary valve RF.
- the compressor 10 is prevented from enlarging the body size in both the axial direction and the radial direction if the front rotary valve RF is provided in the compressor 10 , which includes the suction chamber 17 formed in the cylinder block 11 .
- a rotary valve is used instead of a suction valve to draw refrigerant, and the front cylinder bores 28 are mechanically communicated with the front suction chamber 17 .
- three front suction chambers 17 are formed in the cylinder block 11 . This sufficiently ensures volume of the suction chamber, and suppresses the pulsation.
- Each front suction chamber 17 is formed between the front cylinder bores 28 that are adjacent in the circumferential direction of the shaft hole 11 a.
- the suction chamber communication passages 50 a communicate the front suction chambers 17 and the intake groove 22 a of the front rotary valve RF.
- Refrigerant is directly drawn from each front suction chamber 17 into the intake groove 22 a through the corresponding suction chamber communication passage 50 a .
- the refrigerant does not need to be drawn into the suction pressure region of the front housing 13
- the intake groove 22 a does not need to extend from the front housing 13 to the cylinder block 11 in the rotation shaft 22 .
- the rotation shaft 22 is supported by the shaft hole 11 a (sealing surface) at the front and rear of the intake groove 22 a in the axial direction, the bearing area for the rotation shaft 22 is ensured, and the abrasion resistance is increased.
- each rear suction chamber 18 is formed between adjacent rear cylinder bores 29 around the rotation shaft 22 .
- the suction chambers 17 and 18 are arranged in the radial direction of the cylinder blocks 11 and 12 at the front and rear sides. This avoids enlargement of the compressor 10 in the axial direction.
- the front housing 13 includes the front discharge chamber 28 b
- the rear housing 14 includes the rear discharge chamber 29 b.
- the three front discharge chambers 40 are in communication with the front discharge chamber 28 b
- the three rear discharge chambers 42 are in communication with the rear discharge chambers 29 b.
- Each of the discharge chambers 40 and 42 is arranged between adjacent cylinder bores 28 and 29 .
- the discharge chambers 40 and 42 are arranged at the outer side of the suction chambers 17 and 18 in the radial direction of the cylinder blocks 11 and 12 .
- thermally expanded portions are uniformly distributed in the cylinder blocks 11 and 12 along the radial direction. This prevents the double-headed piston 30 from adversely affected by a thermal deformation of the cylinder bores 28 and 29 .
- Each of the discharge chambers 40 and 42 is between the cylinder bores 28 and 29 .
- thermally expanded portions are evenly distributed in the circumferential direction of the cylinder blocks 11 and 12 . This prevents the double-headed piston 30 from being adversely affected by a thermal deformation of the cylinder bores 28 and 29 .
- the suction port 44 is formed in the cylinder block 11 , and the suction passage 43 , which communicates the front suction chamber 17 and the rear suction chamber 18 , is formed in the cylinder blocks 11 and 12 .
- the suction passage 43 which communicates the front suction chamber 17 and the rear suction chamber 18 .
- Pairs of the front suction chamber 17 and rear suction chamber 18 are formed in the axial direction, and pairs of the front discharge chamber 40 and rear discharge chamber 42 are formed in the axial direction. Further, the front rotary valve RF is used for the front cylinder bores 28 , and the rear rotary valve RR is used for the rear cylinder bores 29 .
- the suction structure is the same at the front and rear sides. This prevents the occurrence of vibration and noise that would be caused by a difference in the suction structure between the front and rear sides.
- Each front suction chamber 17 is formed between front cylinder bores 28 , which are adjacent in the circumferential direction around the shaft hole 11 a .
- the suction chamber communication passages 50 a which communicate the front suction chambers 17 and the intake groove 22 a of the front rotary valve RF, and the front bore communicating passages 50 b, which communicating the intake groove 22 a and the front cylinder bores 28 , are formed in the cylinder block 11 .
- Refrigerant is drawn from each front suction chamber 17 into the corresponding front cylinder bore 28 through the suction chamber communication passage 50 a, the intake groove 22 a , and the front bore communication passage 50 b.
- refrigerant is drawn from the front suction chamber 17 to the front cylinder bore 28 within the cylinder block 11 .
- the rotation shaft 22 receives heat generated by sliding friction between the rotation shaft 22 and the shaft holes 11 a and 12 a or the like.
- heat exchange is carried out between the refrigerant and the rotation shaft 22 through the front rotary valve RF when the refrigerant passes through the intake groove 22 a .
- the intake groove 22 a has a short length so that the refrigerant is sufficiently prevented from being heated. This improves the suction efficiency.
- FIGS. 5 to 7 a second embodiment of the present invention will be described with reference to FIGS. 5 to 7 .
- the same constituents as those in the first embodiment are given the same reference numerals and overlapping description thereof is omitted or simplified.
- a first recess 60 corresponding to each front suction chamber 17 is formed at a portion of a first end face 11 b , which is a surface of a cylinder block 11 closer to a front housing 13 , located outside of a shaft hole 11 a.
- the first recess 60 is formed in the cylinder block 11 to extend from an inner wall of each front suction chamber 17 in a radial direction.
- One end of the first recess 60 opens toward the first end face 11 b , which is a surface of the cylinder block 11 in an axial direction, and is connected with an open end of each front suction chamber 17 .
- the other end of the first recess 60 is located in the middle of the front suction chamber 17 in the axial direction, and does not extend through the cylinder block 11 in the axial direction.
- the first recess 60 is depressed from the first end face 11 b toward a second end face 11 c.
- a second recess 61 corresponding to each front suction chamber 17 is formed at the second end face 11 c , which is a surface of the cylinder block 11 closer to the front housing 13 a .
- the second recess 61 is formed in the cylinder block 11 to extend from the inner wall of each front suction chamber 17 in the radial direction.
- One end of the second recess 61 opens toward the second end face 11 c of the cylinder block 11 , and is connected with an open end of the shaft hole 11 a .
- the other end of the second recess 61 is located in the middle of the shaft hole 11 a in the axial direction, and does not extend through the cylinder block 11 in the axial direction.
- the second recess 61 is depressed from the second end face 11 c toward the first end face 11 b .
- An open end of the second recess 61 closer to the second end face 11 c (closer to a swash plate chamber 25 ) is closed by a thrust bearing 26 .
- the first recess 60 and the second recess 61 are connected and in communication with each other thereby forming a suction chamber communication passage 62 .
- One end of the suction chamber communication passage 62 is defined by an open end of the first recess 60 closer to the front suction chamber 17
- the other end of the suction chamber communication passage 62 is defined by an open end of the second recess 61 closer to the shaft hole 11 a.
- the front suction chamber 17 and an intake groove 22 a are communicable through the suction chamber communication passage 62 .
- the first recess 60 and the second recess 61 are formed together with the front suction chamber 17 when the cylinder block 11 is molded.
- FIG. 6 is a diagram showing a front rotary valve RF developed in a circumferential direction.
- An outline shown by a solid line indicates a peripheral surface of the front rotary valve RF and the shaft hole 11 a, which receives and supports the front rotary valve RF.
- the intake groove 22 a is shown in the outline.
- dashed-two dotted line indicates a front bore communication passage 50 b and the suction chamber communication passage 62 (an overlapping region between the first recess 60 and the second recess 61 ).
- the front bore communication passage 50 b opens toward the shaft hole 11 a and communicates with each front cylinder bore 28 .
- the suction chamber communication passage 62 opens toward the shaft hole 11 a and communicates with each front suction chamber 17 .
- the front bore communication passage 50 b and the suction chamber communication passage 62 are alternately arranged in the circumferential direction of the shaft hole 11 a.
- the intake groove 22 a is formed at a portion of the rotation shaft 22 and extends in the circumferential direction.
- the second embodiment has the advantages described below in addition to the same advantages of (1) to (10) of the first embodiment.
- the suction chamber communication passage 62 has a rectangular shape axially elongated. Accordingly, the suction chamber communication passage 62 and the front bore communication passage 50 b are alternately arranged in the shaft hole 11 a and separate from each other so as to ensure sealing ability therebetween.
- the suction chamber communication passage 62 and the adjacent front bore communication passage 50 b only have to communicate with each other by the intake groove 22 a .
- the intake groove 22 a is simply formed at a portion of the rotary valve RF and extends in the circumferential direction.
- the compressor 10 is prevented from enlarging the body size in the axial direction when the front rotary valve RF is provided in the compressor 10 , which includes the suction chamber 17 formed in the cylinder block 11 .
- the suction chamber communication passage 62 is formed together with the front suction chamber 17 when the cylinder block 11 is molded. This reduces time for manufacturing the cylinder block 11 as compared with the case in which the cylinder block 11 is molded and then the cylinder block 11 is subjected to a cutting work by a drill or the like to form the suction chamber communication passage 62 .
- the suction chamber communication passage 62 is formed by combining the first recess 60 extending from the first end face 11 b and the second recess 61 extending from the second end face 11 c . This suppresses an opening area of the second recess 61 as compared with the case in which the suction chamber communication passage is formed only by the second recess 61 . Thus, the open end of the second recess 61 can be closed by the thrust bearing, which is relatively small in size.
- the first and second embodiments may be varied as described hereafter.
- the suction chamber communication passage 62 is formed by combining the first recess 60 extending from the first end face 11 b and the second recess 61 extending from the second end face 11 c , but is not limited to this.
- the suction chamber communication passage may be formed only by a second recess 66 extending from a second end face 11 c of a cylinder block 11 .
- the second recess 66 enables a front suction chamber 17 to directly communicate with an intake groove 22 a.
- an intake pathway for drawing refrigerant gas to the front cylinder bore 28 may have a pathway passing through an in-shaft passage 65 and in communication with the rear housing suction chamber 19 , in addition to a pathway, which extends from the suction chamber communication passage 62 to the front bore communication passage 50 b via the front rotary valve RF.
- refrigerant is drawn not only through the pathway extending from the rear housing suction chamber 19 via the in-shaft passage 65 but also through the pathway extending from the front suction chamber 17 to the front cylinder bore 28 via the suction chamber communication passage 62 .
- the rotation shaft 22 and the rotary valve are reduced in size in the diameter direction, and the body of the entire compressor 10 is reduced in size.
- rotary valves are used at the front and rear sides to drawn refrigerant.
- the rear side may use a suction valve instead of the rotary valve.
- the rear side is not limited in such a manner. Instead, the rear side may also be formed so that the rear suction chambers 18 and the shaft hole 12 a are communicated by communication passages through an intake groove, the shaft hole 12 a and the rear cylinder bores 29 are communicated by intake passages, and refrigerant is drawn from the rear suction chamber 18 into the rear cylinder bores 29 through the communication passages, the intake groove of the rear rotary valve RR, and the intake passages.
- the suction port 44 is formed in the front cylinder block 11 .
- the suction port 44 may be formed in another portions in the housing H, for example, in the rear cylinder block 12 .
- the refrigerant that has passed through the suction port 44 is supplied to the front suction chambers 17 and the rear suction chambers 18 through the suction passage 43 formed in the cylinder blocks 11 and 12 .
- the refrigerant that passes through the suction port 44 may be supplied to the front suction chambers 17 and the rear suction chambers 18 through the swash plate chamber 25 .
- each of the three front discharge chambers 40 is arranged between adjacent front cylinder bores 28 .
- the front discharge chambers 40 may be collectively formed at one or two locations.
- a part of the intake groove 22 a is formed to have a ring shape that extend along an entire peripheral surface of the rotation shaft 22 closer to a front end of the compressor.
- each of the three rear discharge chambers 42 is arranged between adjacent rear cylinder bores 29 .
- the rear discharge chambers 42 may be collectively formed at one or two locations.
- each rear suction chamber 18 is arranged between adjacent rear cylinder bores 29 .
- the rear suction region may be formed by just the rear housing suction chamber 19 , and the rear suction chamber 18 may be collectively formed at one or two locations.
- the front suction chamber 17 that is in communication with the suction passage 43 has a greater volume than the other two front suction chambers 17 .
- the volume of each of the other two front suction chambers 17 may be greater than the volume of the front suction chamber 17 that is in communication with the suction passage 43 .
- refrigerant is directly supplied from the suction passage 43 .
- the front suction chambers 17 that are in communication with the suction passage 43 may have a small volume so that the refrigerant is smoothly supplied to the front cylinder bores 28 .
- refrigerant is first supplied to the accommodation chamber 13 c before being supplied to the front cylinder bores 28 .
- refrigerant is smoothly supplied to the front cylinder bores 28 . This ensures a large volume and supplies a greater amount of refrigerant.
- the three front suction chambers 17 may have the same volume.
- the front suction chambers 17 and the front discharge chamber 40 are formed extending over both of the front housing 13 and the cylinder block 11 but may be formed in only the cylinder block 11 .
- the rear suction chambers 18 and the rear discharge chamber 42 are formed extending over both of the rear housing 14 and the cylinder block 12 but may be formed in only the cylinder block 12 .
- the swash plate compressor is embodied in the double-headed piston type swash plate compressor.
- the swash plate compressor may be changed to a single-headed piston type swash plate compressor including a single-headed piston connected with the swash plate 24 instead of the double-headed piston 30 .
- RF . . . front rotary valve serving as rotary valve
- 10 . . . double-headed piston type swash plate compressor 11 and 12 . . . cylinder block, 11 a and 12 a . . . shaft hole, 17 . . . front suction chamber, 18 . . . rear suction chamber, 22 . . . rotation shaft, 22 a . . . intake groove, 24 . . . swash plate, 25 . . . swash plate chamber, 26 and 27 . . . thrust bearing, 28 . . . front cylinder bore serving as cylinder bore, 28 b . . . front discharge chamber serving as discharge chamber, 29 . . .
- rear cylinder bore serving as cylinder bore
- 29 b . . . rear discharge chamber serving as discharge chamber
- 30 . . . double-headed piston 32 and 33 . . . external pipe
- 40 . . . front discharge chamber serving s discharge chamber
- 42 . . . rear discharge chamber serving as discharge chamber
- 50 a . . . suction chamber communication passage 50 b . . . front bore communication passage, 60 . . . first recess, 61 and 66 . . . second depression, 62 . . . suction chamber communication passage
Abstract
A swash-plate-type compressor of a double-headed-piston configuration, wherein: a front intake chamber is formed set apart from a swash plate chamber so as to be positioned in a narrow space between circumferentially arranged front cylinder bores; and an intake-chamber-communication path is formed in a cylinder block, the intake-chamber-communication path allowing the front intake chamber and a shaft hole to communicate. A front-bore-communication path is formed on the cylinder block, the communication path allowing each of the plurality of front cylinder bores to communicate with the shaft hole. A front rotary valve is provided on a rotating shaft in which a lead-in groove is formed. The lead-in groove allows the intake-chamber communication path and the front-bore communication path to communicate in the stated order, while the lead-in groove rotates integrally with the rotating shaft. In the compact swash-plate-type compressor any decrease in pulsation or intake efficiency is minimized.
Description
- The present invention relates to a swash plate compressor including a cylinder block having a shaft hole into which a rotary shaft is inserted, and a plurality of cylinder bores located around the shaft hole and arranged along a peripheral direction. The cylinder bores respectively receive pistons.
- For example,
Patent Document 1 describes a double-headed piston type swash plate compressor employing a double-headed piston. As shown inFIG. 11 , aswash plate compressor 80 ofPatent Document 1 includes acylinder block 81 having threecylinder bores 81 a. A double-headed piston 82 is accommodated in each cylinder bore 81 a. Thecylinder block 81 includes asingle suction chamber 83, which is arranged between twoadjacent cylinder bores 81 a, and asingle discharge chamber 84, which is arranged at a different location between twoadjacent cylinder bores 81 a. Thesuction chamber 83 and thedischarge chamber 84 each having a necessary volume to suppress pulsation can be arranged in thecylinder block 81 by effectively using the region betweenadjacent cylinder bores 81 a. This avoids enlargement of theswash plate compressor 80. - Although not shown in the drawing, in the
swash plate compressor 80 ofPatent Document 1, refrigerant is drawn from the suction chamber into thecylinder bores 81 a when a reed type suction valve opens a suction port. When refrigerant is drawn through such a suction valve, the suction valve opens and closes in accordance with the difference in pressure between the interior of the corresponding cylinder bore 81 a and the suction chamber. The suction valve does not open until the pressure in the cylinder bore 81 a decreases to a predetermined pressure. Thus, the suction valve may not open at the desired timing. This may decrease the suction efficiency. - To prevent the suction efficiency from decreasing, the use of a rotary valve that mechanically communicates the suction chamber and cylinder bores is effective for the
swash plate compressor 80 that avoids enlargement. - Patent Document 1: Japanese Laid-Open Patent Publication No. H9-317633
- Patent Document 2: Japanese Laid-Open Patent Publication No. 2007-138925
- Patent Document 3: Japanese Laid-Open Patent Publication No. 2007-270790
- As shown in
FIG. 12 , in aswash plate compressor 90 disclosed inPatent Document 2 that employs a rotary valve, refrigerant is first sent into anaccommodation chamber 93 a (suction chamber) in afront housing 93 through acommunication groove 98 from aswash plate chamber 99. Thus, to guide the refrigerant to ansuction passage 96, which is in communication withcylinder bores 97, the refrigerant in the front housing 93 (accommodation chamber 93 a) is sent toward acylinder block 91 though asupply passage 92 a. More specifically, arotation shaft 92 is must include thesupply passage 92 a, which extends from thefront housing 93 to thecylinder block 91. This lengthens thesupply passage 92 a in the axial direction. Accordingly, in theswash plate compressor 90 ofPatent Document 2, the formation of thesupply passage 92 a enlarges theswash plate compressor 90 in the axial direction. - As shown in
FIG. 13 , aswash plate compressor 100 ofPatent Document 3 that also employs a rotary valve includes arotation shaft 101 having a supplyingpassage 102 formed therein and a conducting hole 101 a for communicating inside and outside of the supplyingpassage 102. Acylinder block 104 includes asuction recess 105 located around therotation shaft 101. The conducting hole 101 a communicates aswash plate chamber 106 with the supplyingpassage 102 through thesuction recess 105. - In the
Patent Document 3, when the suction recess 105 and the conducting hole 101 a are in communication with theswash plate chamber 106, refrigerant in theswash plate chamber 106 flows in the supplyingpassage 102 through thesuction recess 105 and the conducting hole 101 a. The refrigerant further flows from the supplyingpassage 102 tocylinder bores 108 through arotary valve 107. Also inPatent Document 3, the conducting hole 101 a is formed in therotation shaft 101 so that therotation shaft 101 is elongated in the axial direction. Thesuction recess 105 is formed in thecylinder block 104 so that body of the swashplate type compressor 100 enlarges in the axial direction. Therotation shaft 101 having the supplyingpassage 102 needs to be enlarged in a radial direction to ensure the strength in therotation shaft 101. This enlarges the body of the swash plate type compressor in the radial direction. - As discussed above, in the
swash plate compressor swash plate chambers rotary valve 107 and enlarges therotary valve 107. This also enlarges the body of theswash plate compressor - It is an object of the present invention to provide a small swash plate compressor, which suppresses pulsation and prevents the suction efficiency from decreasing.
- To achieve the foregoing object, one aspect of the present invention is a swash plate compressor including a cylinder block, a swash plate, pistons, a rotation shaft and a rotary valve. The cylinder block includes a shaft hole, cylinder bores, a swash plate chamber and a suction chamber. The shaft hole extends through the cylinder block. The cylinder bores are arranged along a circumferential direction around the shaft hole. The suction chamber is arranged in a space between the adjacent cylinder bores and is separated from the swash plate chamber. The swash plate is accommodated in the swash plate chamber. The pistons are connected with the swash plate and respectively arranged in the cylinder bores. The rotation shaft is arranged in the shaft hole and operative to rotate integrally with the swash plate. The rotary valve is provided with the rotation shaft to rotate integrally with the rotation shaft. The cylinder block includes a suction chamber communication passage that defines a communication path between the suction chamber and the shaft hole, and bore communication passages that define independent communication paths between the cylinder bores and the shaft hole. The rotary valve rotates integrally with the rotation shaft to provide sequential communication between the suction chamber communication passage and the bore communication passages.
- Accordingly, the suction chamber and cylinder bores are arranged around the rotary valve along a circumferential direction. Thus, when the rotary valve is employed, body size of the rotary valve and the swash plate compressor are prevented from enlarged. In addition, since the rotary valve is employed, suction efficiency is prevented from being reduced as compared to when a suction valve is employed.
- Preferably, the suction chamber includes a plurality of suction chambers. Each of the plurality of suction chambers is arranged between a circumferentially adjacent pair of the cylinder bores. The suction chamber communication passage includes a plurality of suction chamber communication passages that provide independent communication between the suction chambers and the shaft hole.
- Accordingly, the suction chamber and cylinder bores are alternately arranged around the rotary valve along a circumferential direction. In order to communicate the cylinder bore and the suction chamber via the rotary valve, the intake passage is simply formed at a portion of the rotary valve to extend in the circumferential direction.
- This simplifies the shape of the front rotary valve and therefore further shortens an axial length of the front rotary valve.
- Preferably, the cylinder block includes a plurality of discharge chambers. Each of the discharge chambers is arranged in a space between adjacent cylinder bores.
- Accordingly, when the cylinder blocks are thermally expanded due to the heat of the refrigerant discharged to the discharge chambers, thermally expanded portions are uniformly distributed in the cylinder blocks along the radial direction. This prevents each cylinder bore and each piston from adversely affected by a thermal expansion.
- Preferably, the discharge chambers are arranged outward in a radial direction of the cylinder block from the suction chambers.
- Preferably, the cylinder block includes a suction port to which an external pipe is connected, and a suction passage that provides communication between the suction port and the suction chamber. The suction passage is separated from the swash plate chamber.
- Accordingly, the rotation shaft having a rotary valve receives heat generated by sliding friction due to the rotation of the rotation shaft. In a suction passage from the suction port via the front suction chamber to the front cylinder bore, heat exchange between the refrigerant and the rotation shaft is only carried out when the refrigerant passes through the rotary valve. In addition, an axial length of the rotary valve is shortened so that the refrigerant is sufficiently prevented from being heated. This improves the suction efficiency.
- Preferably, the suction chamber communication passage is a recess formed in an inner wall of the shaft hole. The recess includes an open end in communication with the swash plate chamber. A thrust bearing is arranged between the swash plate and the open end of the recess. The thrust bearing closes the open end of the recess.
- Accordingly, the suction chamber communication passage is formed together with when the cylinder block is molded. This reduces time for manufacturing the cylinder block as compared with the case in which the cylinder block is molded and then the cylinder block is subjected to a cutting work by a drill or the like to form the suction chamber communication passage.
- Preferably, the suction chamber communication passage includes a first recess and a second recess. The first recess is formed in an inner wall of the suction chamber. The first recess includes an open end, which opens toward an end face of the cylinder block in an axial direction. The second recess is formed in an inner wall of the shaft hole. The second recess includes an open end in communication with the swash plate chamber. A thrust bearing is arranged between the swash plate and the open end of the second recess. The thrust bearing closes the open end of the second recess.
- Accordingly, the suction chamber communication passage is formed together with when the cylinder block is molded. In addition, the size of an opening between the suction chamber communication passage and the swash plate chamber is reduced so that the size of the thrust bearing serving as a closing member can be reduced.
- Preferably, the cylinder bores are three cylinder bores.
- This sufficiently ensures volume of the suction chamber, and suppresses the pulsation.
- The present invention provides a swash plate compressor, which is decreased in size while suppresses pulsation and suction efficiency from being lowered.
-
FIG. 1 is a cross-sectional view showing a double-headed piston type swash plate compressor according to a first embodiment of the present invention taken along line 1-1 inFIG. 3 . -
FIG. 2 is a cross-sectional view showing the double-headed piston type swash plate compressor according to the first embodiment taken along line 2-2 inFIG. 3 . -
FIG. 3 is a cross-sectional view showing a front discharge chamber and a front suction chamber taken along line 3-3 inFIG. 1 . -
FIG. 4 is a cross-sectional view taken along line 4-4 ofFIG. 1 showing a front cylinder bore, the front suction chamber and the front discharge chamber. -
FIG. 5 is a partial cross-sectional view showing a double-headed piston type swash plate compressor according to a second embodiment of the present invention. -
FIG. 6 is a development view showing a rotary valve and inside of a shaft hole ofFIG. 5 . -
FIG. 7( a) is a cross-sectional view taken alongline 7 a-7 a ofFIG. 5 showing a cylinder block as viewed from a front suction chamber. -
FIG. 7( b) is a cross-sectional view taken alongline 7 b-7 b ofFIG. 5 showing a cylinder block as viewed from a shaft hole. -
FIG. 8 is a partial cross-sectional view showing a double-headed piston type swash plate compressor of another example. -
FIG. 9 is a cross-sectional view showing a double-headed piston type swash plate compressor of another example. -
FIG. 10 is a development view showing a front rotary valve of another example. -
FIG. 11 is a diagram showing aPatent Document 1. -
FIG. 12 is a diagram showing aPatent Document 2. -
FIG. 13 is a diagram showing aPatent Document 3. - A first embodiment of the present invention that embodies a swash plate compressor in a double-headed piston type
swash plate compressor 10 will now be described with reference toFIGS. 1 to 4 . - As shown in
FIGS. 1 and 2 , a double-headed piston type swash plate compressor 10 (hereinafter simply referred to as the compressor 10) includes a housing H.A cylinder block 11, which is located at a front side (left side as viewed inFIG. 1 ), is coupled to afront housing 13 with a front valve/port formation body 15 arranged in between. Acylinder block 12, which is located at a rear side (right side as viewed inFIG. 1 ), is coupled to arear housing 14 with a rear valve/port formation body 16 arranged in between. The housing H is formed by the twocylinder blocks rear housings - A
rotation shaft 22 is inserted into shaft holes 11 a and 12 a that are respectively formed in the cylinder blocks 11 and 12. Therotation shaft 22 is supported to be rotatable by sealing surfaces defined on the wall surfaces of the shaft holes 11 a and 12 a. Therotation shaft 22 is inserted through insertion holes 15 d and 16 d respectively formed in the centers of the front valve/port formation body 15 and the rear valve/port formation body 16. At an end of therotation shaft 22 projecting from the front valve/port formation body 15, a liptype shaft seal 23 hermetically seals the space between thefront housing 13 and therotation shaft 22. Theshaft seal 23 is accommodated in anaccommodation chamber 13 c defined between the inner wall surface of thefront housing 13 and the circumferential surface of therotation shaft 22. - A
swash plate 24, which rotates integrally with therotation shaft 22, is fixed to therotation shaft 22. Theswash plate 24 is arranged in thecylinder block swash plate chamber 25, which is formed between the cylinder blocks 11 and 12. Athrust bearing 26 is arranged between thefront cylinder block 11 and anannular base 24 a of theswash plate 24. Athrust bearing 27 is arranged between therear cylinder block 12 and the base 24 a of theswash plate 24. Therotation shaft 22 has an axis L. Thethrust bearings swash plate 24 to restrict movement of theswash plate 24 along the axial direction. Thethrust bearings - As shown in
FIG. 4 , three front cylinder bores 28 are arranged around therotation shaft 22 in thefront cylinder block 11. Further, referring toFIG. 1 , three rear cylinder bores 29 are arranged around therotation shaft 22 in therear cylinder block 12. Each front cylinder bore 28 is paired with one of the rear cylinder bores 29. The front and rear cylinder bores 28 and 29 in each pair are aligned with each other in the axial direction (front to rear direction) in which the axis L extends. A double-headedpiston 30 serving as a piston is inserted in each pair of the cylinder bore 28 and 29. The front cylinder bore 28 is closed by the front valve/port formation body 15 and the corresponding double-headedpiston 30, and the rear cylinder bore 29 is closed by the rear valve/port formation body 16 and the corresponding double-headedpiston 30. - Two
shoes 31 arranged on opposite sides of theswash plate 24 transmit the rotational movement of theswash plate 24, which rotates integrally with therotation shaft 22, to the double-headedpistons 30. This reciprocates each double-headedpiston 30 in the corresponding front and rear cylinder bores 28 and 29. Afront compression chamber 28 a is defined in the front cylinder bore 28 by the double-headedpiston 30 and the front valve/port formation body 15, and arear compression chamber 29 a is defined in the rear cylinder bore 29 by the double-headedpiston 30 and the rear valve/port formation body 16. - The
front housing 13 andcylinder block 11 include threefront suction chambers 17, which surround therotation shaft 22 and extend through the front valve/port formation body 15 in. As shown inFIG. 4 , each of the threefront suction chambers 17 are arranged between the front cylinder bores 28 that are circumferentially adjacent around theshaft hole 11 a. The threefront suction chambers 17 are arranged at equal interval at the outer side of theshaft hole 11 a. - As shown in
FIGS. 1 and 2 , one of the threefront suction chambers 17 has a longer length in the axial direction of therotation shaft 22 and a greater volume than the other twofront suction chambers 17. As shown inFIG. 3 , each of the threefront suction chambers 17 is in communication with theaccommodation chamber 13 c of thefront housing 13. Thus, the threefront suction chambers 17 are in communication with one another about theaccommodation chamber 13 c. This forms a single continuous space. - As shown in
FIGS. 1 and 3 , afront discharge chamber 28 b is defined around therotation shaft 22 between thefront housing 13 and the front valve/port formation body 15. Thefront discharge chamber 28 b is a region into which the refrigerant from the threefront compression chambers 28 a is discharged. Further, thefront discharge chamber 28 b is annular and defined in the peripheral portion of thefront housing 13. - In the
front discharge chamber 28 b, each portion facing one of thefront compression chambers 28 a through the front valve/port formation body 15 forms an opening. In thefront discharge chamber 28 b, the portions facing thefront compression chambers 28 a are in communication with one another through passages. This forms a single continuous space. - As shown in
FIGS. 3 and 4 , threefront discharge chambers 40, which are in communication with thefront discharge chamber 28 b, are defined in thecylinder block 11. Thefront discharge chambers 40 extend from thefront cylinder block 11 and through the front valve/port formation body 15. The threefront discharge chambers 40 are arranged around therotation shaft 22. Eachfront discharge chamber 40 is formed between the front cylinder bores 28 that are adjacent in the circumferential direction of theshaft hole 11 a. Further, thefront discharge chambers 40 are located outward in the radial direction of thecylinder block 11 from thefront suction chambers 17. - As shown in
FIGS. 1 and 3 , the front valve/port formation body 15 includesdischarge ports 15 a, which are arranged in correspondence with the front cylinder bores 28, and dischargevalves 15 b, which are arranged in correspondence with thedischarge ports 15 a. Further, the front valve/port formation body 15 includesretainers 15 c, which restrict the open amount of thecorresponding discharge valves 15 b. - The rear structure will now be described.
- As shown in
FIGS. 1 and 2 , threerear suction chambers 18 are arranged around the rotation shaft 22 (shaft hole 12 a) and extend through the rear valve/port formation body 16 in therear housing 14 and thecylinder block 12. In the same manner as the front side, each of the threerear suction chambers 18 is arranged in a space between the rear cylinder bores 29 that are adjacent in the circumferential direction of theshaft hole 12 a. One of the threerear suction chambers 18 has a longer length in the axial direction of therotation shaft 22 and a greater volume than the other tworear suction chambers 18. - A rear
housing suction chamber 19 is defined between a central part of therear housing 14 and the rear valve/port formation body 16. The threerear suction chambers 18 are in communication with one another in the rearhousing suction chamber 19. Thus, the threerear suction chambers 18 are in continuous communication with one another about the rearhousing suction chamber 19. Eachfront suction chamber 17 is paired with one of therear suction chambers 18. Thefront suction chamber 17 andrear suction chamber 18 in each pair are aligned in the front to rear direction in which the axis L extends. Thefront suction chamber 17 andrear suction chamber 18 are formed at opposite sides of theswash plate 24 in the cylinder blocks 11 and 12. - An annular
rear discharge chamber 29 b is defined around therotation shaft 22 between therear housing 14 and the rear valve/port formation body 16. Therear discharge chamber 29 b is a region into which the refrigerant from the threerear compression chambers 29 a is discharged. Further, therear discharge chamber 29 b is defined at the outer side of the rearhousing suction chamber 19. In therear discharge chamber 29 b, each portion facing one of the rear cylinder bores 29 through the rear valve/port formation body 16 forms an opening having a size that conforms to the circularrear compression chamber 29 a. In therear discharge chamber 29 b, the portions facing the rear cylinder bores 29 are in communication with one another through passages. This forms a single continuous space. - The
cylinder block 12 includes threerear discharge chamber 42, which are in communication with therear discharge chamber 29 b. Therear discharge chambers 42 extend from therear housing 14 through the rear valve/port formation body 16 and to therear cylinder block 12. The threerear discharge chambers 42 are arranged around theshaft hole 12 a and formed between the rear cylinder bores 29 that are adjacent in the circumferential direction of theshaft hole 12 a. Therear discharge chambers 42 are formed outward in the radial direction of thecylinder block 12 from therear suction chambers 18. Eachfront discharge chamber 28 b is paired with one of therear discharge chambers 29 b. Thefront discharge chamber 28 b andrear discharge chamber 29 b in each pair are aligned in the front to rear direction in which the axis L extends. - As shown in
FIG. 1 , the rear valve/port formation body 16 includes discharge ports 16 a, which are arranged in correspondence with therear discharge chambers 29 b, and dischargevalves 16 b, which are arranged in correspondence with the discharge ports 16 a. Further, the rear valve/port formation body 16 includesretainers 16 c, which restrict the open amount of thedischarge valves 16 b. - A
suction passage 43 is formed in the cylinder blocks 11 and 12. Thesuction passage 43 has a front opening, which is in communication with thefront suction chamber 17 having the largest volume, and a rear opening, which is in communication with therear suction chamber 18 having the largest volume. Further, asuction port 44 is formed in thefront cylinder block 11. Thesuction port 44 has one end that opens in the outer surface of thecylinder block 11 and another end that opens in the wall surface of thesuction passage 43. Anexternal pipe 32 of an external refrigerant circuit that is arranged outside thecompressor 10 is connected to one open end of thesuction port 44. Thesuction passage 43 is formed in the cylinder blocks 11 and 12 and separated from theswash plate chamber 25. - The
suction passage 43 is formed in communication with the front andrear suction chambers suction passage 43 is sandwiched in the axial direction by thefront discharge chamber 40 and therear discharge chamber 42, which are located at the outer sides of thesuction chambers - As shown in
FIG. 2 , adischarge passage 45 is formed in the cylinder blocks 11 and 12. Thedischarge passage 45 has a front opening, which is in communication with one of the threefront discharge chambers 40, and a rear opening, which is in communication with one of the threerear discharge chambers 42. Further, adischarge port 46 is formed in thecylinder block 11. Thedischarge port 46 has one end that opens in the outer surface of thecylinder block 11 and another end that opens in the wall surface of thedischarge passage 45. Theexternal pipe 33 of the external refrigerant circuit that is arranged outside thecompressor 10, is connected to thedischarge port 46. - As shown in
FIG. 3 , in the cylinder blocks 11 and 12, thedischarge passage 45 is separated in the circumferential direction of the cylinder blocks 11 and 12 from thesuction passage 43. More specifically, thefront discharge chamber 40 andrear discharge chamber 42 sandwiching thedischarge passage 45 in the axial direction is separated in the circumferential direction from thefront discharge chamber 40 andrear discharge chamber 42 sandwiching thesuction passage 43 in the axial direction. - When forming a refrigerating cycle for a vehicle air conditioner with the
compressor 10, the external refrigerant circuit connects thedischarge port 46 and thesuction port 44 of thecompressor 10 via theexternal pipes discharge port 46 of thecompressor 10 in the external refrigerant circuit. - The suction structure of the
compressor 10 will now be described. - First, a front suction structure will be described. As shown in
FIG. 4 , suctionchamber communication passages 50 a communicating thefront suction chambers 17 and theshaft hole 11 a are formed in thecylinder block 11. Each suctionchamber communication passage 50 a has one end that opens in the correspondingfront suction chamber 17 and another end that opens in the sealing surface of the wall defining theshaft hole 11 a. The suctionchamber communication passages 50 a formed in thecylinder block 11 extend slightly inclined relative to the radial direction of thecylinder block 11. - Front bore
communication passages 50 b communicating theshaft hole 11 a and the front cylinder bores 28 are formed in thecylinder block 11. Each frontbore communication passage 50 b has one end that opens in the sealing surface of the wall defining theshaft hole 11 a and another end that opens in the corresponding front cylinder bore 28. The suctionchamber communication passages 50 a and front borecommunication passages 50 b are alternately arranged in the circumferential direction of theshaft hole 11 a. - As shown in
FIGS. 1 and 4 , anintake groove 22 a is formed in the circumferential surface of the front side of therotation shaft 22. Theintake groove 22 a is recessed in the circumferential surface of therotation shaft 22, which is a solid shaft, at the side closer to thefront housing 13. Theintake groove 22 a opens towards the sealing surface of the wall defining theshaft hole 11 a and is independently communicable with the suctionchamber communication passages 50 a and the frontbore communication passages 50 b. Rotation of therotation shaft 22 changes the position of theintake groove 22 a. This mechanically switches the suctionchamber communication passages 50 a and front borecommunication passages 50 b that come into communication with theintake groove 22 a. - The portion of the
rotation shaft 22 surrounded by the sealing surface forms a front rotary valve RF, which is formed integrally with therotation shaft 22. Theintake groove 22 a communicates one of the suctionchamber communication passage 50 a and the frontbore communication passage 50 b that is adjacent in the circumferential direction of theshaft hole 11 a. As therotation shaft 22 rotates, the suctionchamber communication passage 50 a and frontbore communication passage 50 b that are independently in communication through theintake groove 22 a draw in refrigerant from the correspondingfront suction chamber 17 to the adjacent front cylinder bore 28. In the present embodiment, theintake groove 22 a serves as a supplying passage, which communicates the front cylinder bore 28 and thefront suction chamber 17 in the front rotary valve RF. - The rear intake structure will now be described.
- As shown in
FIGS. 1 and 2 ,rear intake passages 51 communicating the rear cylinder bores 29 and theshaft hole 12 a are formed in thecylinder block 12. Eachrear intake passage 51 has one end that opens in the corresponding rear cylinder bore 29 and another end that opens in the sealing surface of the wall defining theshaft hole 12 a. Asupply passage 22 b is formed in the circumferential surface of the rear side of therotation shaft 22. Thesupply passage 22 b has one end that opens in the rearhousing suction chamber 19 of therear housing 14 and another end that is communicable with therear intake passages 51. Rotation of therotation shaft 22 changes the position of thesupply passage 22 b. This mechanically switches therear intake passages 51 that come into communication with thesupply passage 22 b. The portion of therotation shaft 22 surrounded by the sealing surface forms a rear rotary valve RR, which is formed integrally with therotation shaft 22. - The operation of the
compressor 10 will now be described. - Refrigerant is drawn through the
suction port 44 into thesuction passage 43 and supplied to eachfront suction chamber 17 and eachrear suction chamber 18. When each front cylinder bore 28 performs the intake stroke, one of the suctionchamber communication passages 50 a and the adjacent front borecommunication passage 50 b come into communication through theintake groove 22 a of the front rotary valve RF, as shown inFIG. 4 . The refrigerant is then drawn from thefront suction chamber 17 through the front rotary valve RF into the corresponding front cylinder bore 28. - As the
rotation shaft 22 further rotates, theintake groove 22 a goes out of communication with the suctionchamber communication passage 50 a. In this state, the suctionchamber communication passage 50 a and the frontbore communication passage 50 b are not in communication with each other, and the front cylinder bore 28 is closed. Then, the front cylinder bore 28 performs the compression stroke and discharge stroke. The refrigerant in thefront compression chamber 28 a is forced through thedischarge valve 15 b from thedischarge port 15 a and discharged to thefront discharge chamber 28 b. The refrigerant discharged to thefront discharge chamber 28 b flows out of thefront discharge chamber 40 through thedischarge passage 45 and thedischarge port 46 and into the external refrigerant circuit. - At the rear side, when each rear cylinder bore 29 performs the intake stroke in a state in which refrigerant is supplied to the rear
housing suction chamber 19, thesupply passage 22 b, which is in communication with the rearhousing suction chamber 19 in the rear rotary valve RR, comes into communication with one or tworear intake passage 51. This supplies refrigerant to therear intake passage 51 from the rearhousing suction chamber 19 through the rear rotary valve RR, and the refrigerant is drawn into the rear cylinder bore 29, which is in communication with therear intake passage 51. - As the
rotation shaft 22 further rotates, thesupply passage 22 b goes out of communication with therear intake passage 51. In this state, therear intake passage 51 and the rearhousing suction chamber 19 are not in communication with each other, and the rear cylinder bore 29 is closed. - Then, the rear cylinder bore 29 performs the compression stroke and the discharge stroke. The refrigerant in the
rear compression chamber 29 a is forced through thedischarge valve 16 b from the discharge port 16 a and discharged to therear discharge chamber 29 b. The refrigerant discharged to therear discharge chamber 29 b flows out of therear discharge chamber 42 through thedischarge passage 45 and thedischarge port 46 and into the external refrigerant circuit. - Accordingly, the present embodiment has the advantages described below.
- (1) In the double-headed piston type
swash plate compressor 10, the three front cylinder bores 28 are formed around theshaft hole 11 a of thecylinder block 11, and eachfront suction chamber 17 is arranged between the front cylinder bores 28 that are adjacent to each other. That is, the front cylinder bores 28 and thefront suction chambers 17 are alternately arranged around theshaft hole 11 a. In addition, the suctionchamber communication passages 50 a, which communicatesfront suction chambers 17 with theshaft hole 11 a, and the frontbore communication passages 50 b, which communicates the front cylinder bores 28 with theshaft hole 11 a, are formed in thecylinder block 11. The suctionchamber communication passages 50 a and the frontbore communication passages 50 b are alternately arranged in the circumferential direction of theshaft hole 11 a. In thecylinder block 11, the refrigerant in eachfront suction chamber 17 is directly drawn into theintake groove 22 a through the corresponding suctionchamber communication passage 50 a, and then drawn in the front cylinder bore 28 through the frontbore communication passage 50 b. - Accordingly, in order to communicate the front cylinder bore 28 and the circumferentially adjacent
front suction chamber 17 via the rotary valve RF, theintake groove 22 a is simply formed at a portion of the rotary valve RF to extend in the circumferential direction. This simplifies the shape of the front rotary valve RF and therefore shortens an axial length of the front rotary valve RF. Thus, thecompressor 10 is prevented from enlarging the body size in both the axial direction and the radial direction if the front rotary valve RF is provided in thecompressor 10, which includes thesuction chamber 17 formed in thecylinder block 11. In this manner, a rotary valve is used instead of a suction valve to draw refrigerant, and the front cylinder bores 28 are mechanically communicated with thefront suction chamber 17. This prevents the suction efficiency from decreasing and is in contrast with a suction valve. In addition, threefront suction chambers 17 are formed in thecylinder block 11. This sufficiently ensures volume of the suction chamber, and suppresses the pulsation. - (2) Each
front suction chamber 17 is formed between the front cylinder bores 28 that are adjacent in the circumferential direction of theshaft hole 11 a. In thecylinder block 11, the suctionchamber communication passages 50 a communicate thefront suction chambers 17 and theintake groove 22 a of the front rotary valve RF. Refrigerant is directly drawn from eachfront suction chamber 17 into theintake groove 22 a through the corresponding suctionchamber communication passage 50 a. Thus, the refrigerant does not need to be drawn into the suction pressure region of thefront housing 13, and theintake groove 22 a does not need to extend from thefront housing 13 to thecylinder block 11 in therotation shaft 22. In this manner, therotation shaft 22 is supported by theshaft hole 11 a (sealing surface) at the front and rear of theintake groove 22 a in the axial direction, the bearing area for therotation shaft 22 is ensured, and the abrasion resistance is increased. - (3) In the same manner as the
front suction chambers 17, eachrear suction chamber 18 is formed between adjacent rear cylinder bores 29 around therotation shaft 22. Thus, thesuction chambers compressor 10 in the axial direction. - (4) The
front housing 13 includes thefront discharge chamber 28 b, and therear housing 14 includes therear discharge chamber 29 b. The threefront discharge chambers 40 are in communication with thefront discharge chamber 28 b, and the threerear discharge chambers 42 are in communication with therear discharge chambers 29 b. Each of thedischarge chambers discharge chambers - (5) The
discharge chambers suction chambers discharge chambers piston 30 from adversely affected by a thermal deformation of the cylinder bores 28 and 29. - (6) Each of the
discharge chambers discharge chambers piston 30 from being adversely affected by a thermal deformation of the cylinder bores 28 and 29. - (7) The
suction port 44 is formed in thecylinder block 11, and thesuction passage 43, which communicates thefront suction chamber 17 and therear suction chamber 18, is formed in the cylinder blocks 11 and 12. Thus, when refrigerant is drawn into thesuction chambers swash plate chamber 25. This prevents the refrigerant that is drawn into thesuction chambers rotation shaft 22 heated by a sliding friction in theswash plate chamber 25. - (8) Pairs of the
front suction chamber 17 andrear suction chamber 18 are formed in the axial direction, and pairs of thefront discharge chamber 40 andrear discharge chamber 42 are formed in the axial direction. Further, the front rotary valve RF is used for the front cylinder bores 28, and the rear rotary valve RR is used for the rear cylinder bores 29. Thus, the suction structure is the same at the front and rear sides. This prevents the occurrence of vibration and noise that would be caused by a difference in the suction structure between the front and rear sides. - (9) Each
front suction chamber 17 is formed between front cylinder bores 28, which are adjacent in the circumferential direction around theshaft hole 11 a. The suctionchamber communication passages 50 a, which communicate thefront suction chambers 17 and theintake groove 22 a of the front rotary valve RF, and the frontbore communicating passages 50 b, which communicating theintake groove 22 a and the front cylinder bores 28, are formed in thecylinder block 11. Refrigerant is drawn from eachfront suction chamber 17 into the corresponding front cylinder bore 28 through the suctionchamber communication passage 50 a, theintake groove 22 a, and the frontbore communication passage 50 b. Thus, refrigerant is drawn from thefront suction chamber 17 to the front cylinder bore 28 within thecylinder block 11. This reduces a contacting area between the refrigerant and theintake groove 22 a compared to when the refrigerant is drawn into the front cylinder bores 28 through a groove, which extends into thefront housing 13 and theswash plate chamber 25. This reduces suction heating that would be caused when the contacting area is large, and prevents the suction efficiency from decreasing. - (10) The
rotation shaft 22 receives heat generated by sliding friction between therotation shaft 22 and the shaft holes 11 a and 12 a or the like. In a suction passage from thesuction port 44 via thefront suction chamber 17 to the front cylinder bore 28, heat exchange is carried out between the refrigerant and therotation shaft 22 through the front rotary valve RF when the refrigerant passes through theintake groove 22 a. Theintake groove 22 a has a short length so that the refrigerant is sufficiently prevented from being heated. This improves the suction efficiency. - Next, a second embodiment of the present invention will be described with reference to
FIGS. 5 to 7 . The same constituents as those in the first embodiment are given the same reference numerals and overlapping description thereof is omitted or simplified. - As shown in
FIGS. 5 and 7( a), afirst recess 60 corresponding to eachfront suction chamber 17 is formed at a portion of afirst end face 11 b, which is a surface of acylinder block 11 closer to afront housing 13, located outside of ashaft hole 11 a. Thefirst recess 60 is formed in thecylinder block 11 to extend from an inner wall of eachfront suction chamber 17 in a radial direction. One end of thefirst recess 60 opens toward thefirst end face 11 b, which is a surface of thecylinder block 11 in an axial direction, and is connected with an open end of eachfront suction chamber 17. The other end of thefirst recess 60 is located in the middle of thefront suction chamber 17 in the axial direction, and does not extend through thecylinder block 11 in the axial direction. Thefirst recess 60 is depressed from thefirst end face 11 b toward asecond end face 11 c. - As shown in
FIGS. 5 and 7( b), asecond recess 61 corresponding to eachfront suction chamber 17 is formed at thesecond end face 11 c, which is a surface of thecylinder block 11 closer to the front housing 13 a. Thesecond recess 61 is formed in thecylinder block 11 to extend from the inner wall of eachfront suction chamber 17 in the radial direction. One end of thesecond recess 61 opens toward thesecond end face 11 c of thecylinder block 11, and is connected with an open end of theshaft hole 11 a. The other end of thesecond recess 61 is located in the middle of theshaft hole 11 a in the axial direction, and does not extend through thecylinder block 11 in the axial direction. Thesecond recess 61 is depressed from thesecond end face 11 c toward thefirst end face 11 b. An open end of thesecond recess 61 closer to thesecond end face 11 c (closer to a swash plate chamber 25) is closed by athrust bearing 26. - In the
cylinder block 11, thefirst recess 60 and thesecond recess 61 are connected and in communication with each other thereby forming a suctionchamber communication passage 62. One end of the suctionchamber communication passage 62 is defined by an open end of thefirst recess 60 closer to thefront suction chamber 17, and the other end of the suctionchamber communication passage 62 is defined by an open end of thesecond recess 61 closer to theshaft hole 11 a. Thefront suction chamber 17 and anintake groove 22 a are communicable through the suctionchamber communication passage 62. An open end of the suctionchamber communication passage 62 closer to theswash plate chamber 25 is closed by thethrust bearing 26, and a clearance between the suctionchamber communication passage 62 and theswash plate chamber 25 is sealed. Thefirst recess 60 and thesecond recess 61 are formed together with thefront suction chamber 17 when thecylinder block 11 is molded. -
FIG. 6 is a diagram showing a front rotary valve RF developed in a circumferential direction. An outline shown by a solid line indicates a peripheral surface of the front rotary valve RF and theshaft hole 11 a, which receives and supports the front rotary valve RF. Theintake groove 22 a is shown in the outline. InFIG. 6 , dashed-two dotted line indicates a frontbore communication passage 50 b and the suction chamber communication passage 62 (an overlapping region between thefirst recess 60 and the second recess 61). The frontbore communication passage 50 b opens toward theshaft hole 11 a and communicates with each front cylinder bore 28. The suctionchamber communication passage 62 opens toward theshaft hole 11 a and communicates with eachfront suction chamber 17. - As shown in
FIG. 6 , the frontbore communication passage 50 b and the suctionchamber communication passage 62 are alternately arranged in the circumferential direction of theshaft hole 11 a. In order to communicate the suctionchamber communication passage 62 and the frontbore communication passage 50 b via theintake groove 22 a, theintake groove 22 a is formed at a portion of therotation shaft 22 and extends in the circumferential direction. - Accordingly, the second embodiment has the advantages described below in addition to the same advantages of (1) to (10) of the first embodiment.
- (11) The suction
chamber communication passage 62 has a rectangular shape axially elongated. Accordingly, the suctionchamber communication passage 62 and the frontbore communication passage 50 b are alternately arranged in theshaft hole 11 a and separate from each other so as to ensure sealing ability therebetween. Thus, in order to communicate the front cylinder bore 28 and the circumferentially adjacentfront suction chamber 17 via the rotary valve RF, the suctionchamber communication passage 62 and the adjacent front borecommunication passage 50 b only have to communicate with each other by theintake groove 22 a. For this, theintake groove 22 a is simply formed at a portion of the rotary valve RF and extends in the circumferential direction. This simplifies the shape of the front rotary valve RF formed in therotation shaft 22 and therefore shortens an axial length of the front rotary valve RF. Thus, thecompressor 10 is prevented from enlarging the body size in the axial direction when the front rotary valve RF is provided in thecompressor 10, which includes thesuction chamber 17 formed in thecylinder block 11. - (12) The suction
chamber communication passage 62 is formed together with thefront suction chamber 17 when thecylinder block 11 is molded. This reduces time for manufacturing thecylinder block 11 as compared with the case in which thecylinder block 11 is molded and then thecylinder block 11 is subjected to a cutting work by a drill or the like to form the suctionchamber communication passage 62. - (13) The suction
chamber communication passage 62 is formed by combining thefirst recess 60 extending from thefirst end face 11 b and thesecond recess 61 extending from thesecond end face 11 c. This suppresses an opening area of thesecond recess 61 as compared with the case in which the suction chamber communication passage is formed only by thesecond recess 61. Thus, the open end of thesecond recess 61 can be closed by the thrust bearing, which is relatively small in size. - The first and second embodiments may be varied as described hereafter.
- In the embodiment described above, the suction
chamber communication passage 62 is formed by combining thefirst recess 60 extending from thefirst end face 11 b and thesecond recess 61 extending from thesecond end face 11 c, but is not limited to this. As shown inFIG. 8 , in case that thethrust bearing 26 has a diameter, which is sufficiently large, the suction chamber communication passage may be formed only by asecond recess 66 extending from asecond end face 11 c of acylinder block 11. Thesecond recess 66 enables afront suction chamber 17 to directly communicate with anintake groove 22 a. - As shown in
FIG. 9 , an intake pathway for drawing refrigerant gas to the front cylinder bore 28 may have a pathway passing through an in-shaft passage 65 and in communication with the rearhousing suction chamber 19, in addition to a pathway, which extends from the suctionchamber communication passage 62 to the frontbore communication passage 50 b via the front rotary valve RF. According to this configuration, refrigerant is drawn not only through the pathway extending from the rearhousing suction chamber 19 via the in-shaft passage 65 but also through the pathway extending from thefront suction chamber 17 to the front cylinder bore 28 via the suctionchamber communication passage 62. This reduces size of the diameter of the in-shaft passage 65. Thus, therotation shaft 22 and the rotary valve are reduced in size in the diameter direction, and the body of theentire compressor 10 is reduced in size. - In the embodiment described above, rotary valves are used at the front and rear sides to drawn refrigerant. However, the rear side may use a suction valve instead of the rotary valve.
- In the embodiment described above, at the rear side, refrigerant of the
rear suction chambers 18 is collected in the rearhousing suction chambers 19. Then, the refrigerant is drawn from the rearhousing suction chambers 19 into the rear cylinder bores 29 through the rear rotary valve RR. However, the rear side is not limited in such a manner. Instead, the rear side may also be formed so that therear suction chambers 18 and theshaft hole 12 a are communicated by communication passages through an intake groove, theshaft hole 12 a and the rear cylinder bores 29 are communicated by intake passages, and refrigerant is drawn from therear suction chamber 18 into the rear cylinder bores 29 through the communication passages, the intake groove of the rear rotary valve RR, and the intake passages. - In the embodiment described above, the
suction port 44 is formed in thefront cylinder block 11. Thesuction port 44 may be formed in another portions in the housing H, for example, in therear cylinder block 12. - In the embodiment described above, the refrigerant that has passed through the
suction port 44 is supplied to thefront suction chambers 17 and therear suction chambers 18 through thesuction passage 43 formed in the cylinder blocks 11 and 12. However, the refrigerant that passes through thesuction port 44 may be supplied to thefront suction chambers 17 and therear suction chambers 18 through theswash plate chamber 25. - In the embodiment described above, each of the three
front discharge chambers 40 is arranged between adjacent front cylinder bores 28. However, thefront discharge chambers 40 may be collectively formed at one or two locations. In this configuration, as shown inFIG. 10 , a part of theintake groove 22 a is formed to have a ring shape that extend along an entire peripheral surface of therotation shaft 22 closer to a front end of the compressor. - Further, each of the three
rear discharge chambers 42 is arranged between adjacent rear cylinder bores 29. However, therear discharge chambers 42 may be collectively formed at one or two locations. - In the embodiment described above, three
rear suction chambers 18 are formed, and eachrear suction chamber 18 is arranged between adjacent rear cylinder bores 29. Instead, the rear suction region may be formed by just the rearhousing suction chamber 19, and therear suction chamber 18 may be collectively formed at one or two locations. - In the embodiment described above, the
front suction chamber 17 that is in communication with thesuction passage 43 has a greater volume than the other twofront suction chambers 17. Instead, the volume of each of the other twofront suction chambers 17 may be greater than the volume of thefront suction chamber 17 that is in communication with thesuction passage 43. In such a structure, refrigerant is directly supplied from thesuction passage 43. Thus, thefront suction chambers 17 that are in communication with thesuction passage 43 may have a small volume so that the refrigerant is smoothly supplied to the front cylinder bores 28. In contrast, in the other twofront suction chambers 17, refrigerant is first supplied to theaccommodation chamber 13 c before being supplied to the front cylinder bores 28. Thus, refrigerant is smoothly supplied to the front cylinder bores 28. This ensures a large volume and supplies a greater amount of refrigerant. - The three
front suction chambers 17 may have the same volume. - In the embodiment described above, the
front suction chambers 17 and thefront discharge chamber 40 are formed extending over both of thefront housing 13 and thecylinder block 11 but may be formed in only thecylinder block 11. - In the embodiment described above, the
rear suction chambers 18 and therear discharge chamber 42 are formed extending over both of therear housing 14 and thecylinder block 12 but may be formed in only thecylinder block 12. - In the embodiment described above, the swash plate compressor is embodied in the double-headed piston type swash plate compressor. However, the swash plate compressor may be changed to a single-headed piston type swash plate compressor including a single-headed piston connected with the
swash plate 24 instead of the double-headedpiston 30. - Explanation of Reference Numerals
- RF . . . front rotary valve serving as rotary valve, 10 . . . double-headed piston type swash plate compressor, 11 and 12 . . . cylinder block, 11 a and 12 a . . . shaft hole, 17 . . . front suction chamber, 18 . . . rear suction chamber, 22 . . . rotation shaft, 22 a . . . intake groove, 24 . . . swash plate, 25 . . . swash plate chamber, 26 and 27 . . . thrust bearing, 28 . . . front cylinder bore serving as cylinder bore, 28 b . . . front discharge chamber serving as discharge chamber, 29 . . . rear cylinder bore serving as cylinder bore, 29 b . . . rear discharge chamber serving as discharge chamber, 30 . . . double-headed piston, 32 and 33 . . . external pipe, 40 . . . front discharge chamber serving s discharge chamber, 42 . . . rear discharge chamber serving as discharge chamber, 43 . . . suction passage, 44 . . . suction port, 50 a . . . suction chamber communication passage, 50 b . . . front bore communication passage, 60 . . . first recess, 61 and 66 . . . second depression, 62 . . . suction chamber communication passage
Claims (8)
1. A swash plate compressor comprising:
a cylinder block including a shaft hole, cylinder bores, a swash plate chamber and a suction chamber, wherein the shaft hole extends through the cylinder block, the cylinder bores are arranged along a circumferential direction around the shaft hole, and the suction chamber is arranged in a space between the adjacent cylinder bores and is separated from the swash plate chamber;
a swash plate accommodated in the swash plate chamber;
pistons connected with the swash plate and respectively arranged in the cylinder bores;
a rotation shaft arranged in the shaft hole and operative to rotate integrally with the swash plate; and
a rotary valve provided with the rotation shaft to rotate integrally with the rotation shaft;
wherein the cylinder block includes a suction chamber communication passage that defines a communication path between the suction chamber and the the shaft hole, and bore communication passages that define independent communication paths between the cylinder bores and the shaft hole,
wherein the rotary valve rotates integrally with the rotation shaft to provide sequential communication between the suction chamber communication passage and the bore communication passages.
2. The swash plate compressor according to claim 1 , wherein
the suction chamber includes a plurality of suction chambers, each of the plurality of suction chambers is arranged between a circumferentially adjacent pair of the cylinder bores,
the suction chamber communication passage includes a plurality of suction chamber communication passages that provide independent communication between the suction chambers and the shaft hole.
3. The swash plate compressor according to claim 2 , wherein
the cylinder block includes a plurality of discharge chambers, each of the discharge chambers is arranged in a space between adjacent cylinder bores.
4. The swash plate compressor according to claim 3 , wherein the discharge chambers are arranged outward in a radial direction of the cylinder block from the suction chambers.
5. The swash plate compressor according to claim 1 , wherein
the cylinder block includes a suction port to which an external pipe is connected, and a suction passage that provides communication between the suction port and the suction chamber,
the suction passage is separated from the swash plate chamber.
6. The swash plate compressor according to claim 1 , wherein
the suction chamber communication passage is a recess formed in an inner wall of the shaft hole, the recess including an open end in communication with the swash plate chamber,
a thrust bearing is arranged between the swash plate and the open end of the recess, and
the thrust bearing closes the open end of the recess.
7. The swash plate compressor according to claim 1 , wherein
the suction chamber communication passage includes a first recess and a second recess, the first recess formed in an inner wall of the suction chamber, the first recess including an open end, which opens toward an end face of the cylinder block in an axial direction, the second recess formed in an inner wall of the shaft hole, the second recess including an open end in communication with the swash plate chamber,
a thrust bearing is arranged between the swash plate and the open end of the second recess, and
the thrust bearing closes the open end of the second recess.
8. The swash plate compressor according to claim 1 , wherein the cylinder bores are three cylinder bores.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
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JP2011079843 | 2011-03-31 | ||
JP2011-079843 | 2011-03-31 | ||
PCT/JP2012/058407 WO2012133669A1 (en) | 2011-03-31 | 2012-03-29 | Swash-plate-type compressor |
Publications (1)
Publication Number | Publication Date |
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US20130343922A1 true US20130343922A1 (en) | 2013-12-26 |
Family
ID=46931371
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US14/002,801 Abandoned US20130343922A1 (en) | 2011-03-31 | 2012-03-29 | Swash-plate-type compressor |
Country Status (6)
Country | Link |
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US (1) | US20130343922A1 (en) |
JP (1) | JP5574041B2 (en) |
KR (1) | KR101450596B1 (en) |
CN (1) | CN103459846A (en) |
BR (1) | BR112013025034A2 (en) |
WO (1) | WO2012133669A1 (en) |
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Publication number | Priority date | Publication date | Assignee | Title |
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JP5915576B2 (en) * | 2013-03-27 | 2016-05-11 | 株式会社豊田自動織機 | Piston type swash plate compressor |
JP7230762B2 (en) * | 2019-10-02 | 2023-03-01 | 株式会社豊田自動織機 | piston compressor |
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JPH05312146A (en) * | 1992-05-13 | 1993-11-22 | Toyota Autom Loom Works Ltd | Cam plate type compressor |
JPH08135568A (en) * | 1994-11-04 | 1996-05-28 | Toyota Autom Loom Works Ltd | Reciprocation type compressor |
JP2004239067A (en) * | 2003-02-03 | 2004-08-26 | Honda Motor Co Ltd | Rotary fluid machinery |
JP2005163581A (en) * | 2003-12-01 | 2005-06-23 | Honda Motor Co Ltd | Rotating fluid machine |
JP4702145B2 (en) | 2006-03-31 | 2011-06-15 | 株式会社豊田自動織機 | Swash plate compressor |
KR101001575B1 (en) * | 2008-12-09 | 2010-12-17 | 주식회사 두원전자 | swash plate type compressor with rotary valve |
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2012
- 2012-03-29 BR BR112013025034A patent/BR112013025034A2/en not_active IP Right Cessation
- 2012-03-29 JP JP2013507731A patent/JP5574041B2/en not_active Expired - Fee Related
- 2012-03-29 CN CN2012800149814A patent/CN103459846A/en active Pending
- 2012-03-29 US US14/002,801 patent/US20130343922A1/en not_active Abandoned
- 2012-03-29 KR KR1020137025362A patent/KR101450596B1/en not_active IP Right Cessation
- 2012-03-29 WO PCT/JP2012/058407 patent/WO2012133669A1/en active Application Filing
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US3352485A (en) * | 1965-10-22 | 1967-11-14 | Toyoda Automatic Loom Works | Swash plate compressor for use in air conditioning system for vehicles |
US3750848A (en) * | 1970-10-15 | 1973-08-07 | Toyoda Kk | Apparatus for lubricating a rotary swash plate type compressor |
US3801227A (en) * | 1970-10-17 | 1974-04-02 | Toyoda Automatic Loom Works | Swash-plate type compressor for air conditioning of vehicles |
US4273518A (en) * | 1978-10-16 | 1981-06-16 | Diesel Kiki Co., Ltd. | Swash-plate type compressor |
US5207078A (en) * | 1991-09-02 | 1993-05-04 | Kabushiki Kaisha Toyoda Jidoshokki | Reciprocatory piston type compressor for a refrigeration system |
US5267839A (en) * | 1991-09-11 | 1993-12-07 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Reciprocatory piston type compressor with a rotary valve |
US7841840B2 (en) * | 2005-10-17 | 2010-11-30 | Kabushiki Kaisha Toyota Jidoshokki | Double-headed piston type compressor |
US8197229B2 (en) * | 2008-05-29 | 2012-06-12 | Kabushiki Kaisha Toyota Jidoshokki | Double-headed piston type compressor |
US20100003146A1 (en) * | 2008-07-02 | 2010-01-07 | Kabushiki Kaisha Toyota Jidoshokki | Piston type compressor |
Also Published As
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CN103459846A (en) | 2013-12-18 |
JPWO2012133669A1 (en) | 2014-07-28 |
KR20130131450A (en) | 2013-12-03 |
JP5574041B2 (en) | 2014-08-20 |
KR101450596B1 (en) | 2014-10-14 |
WO2012133669A1 (en) | 2012-10-04 |
BR112013025034A2 (en) | 2016-12-27 |
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