WO2012133669A1 - Swash-plate-type compressor - Google Patents
Swash-plate-type compressor Download PDFInfo
- Publication number
- WO2012133669A1 WO2012133669A1 PCT/JP2012/058407 JP2012058407W WO2012133669A1 WO 2012133669 A1 WO2012133669 A1 WO 2012133669A1 JP 2012058407 W JP2012058407 W JP 2012058407W WO 2012133669 A1 WO2012133669 A1 WO 2012133669A1
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- WO
- WIPO (PCT)
- Prior art keywords
- suction
- chamber
- swash plate
- suction chamber
- cylinder block
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- 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 suction valve opens and closes based on the pressure difference between the cylinder bore 81a and the suction chamber, and the suction valve is not opened until the pressure in the cylinder bore 81a has decreased to a predetermined pressure.
- the suction valve may not open at a desired timing without being opened, and the suction efficiency may be deteriorated.
- a rotary valve in which the cylinder bore and the suction chamber are in mechanical communication is employed in order to prevent the deterioration of the suction efficiency with respect to the swash plate compressor 80 disclosed in Patent Document 1 in which the size of the body is suppressed. It is effective.
- a supply passage 92a extending from the front housing 93 to the cylinder block 91 must be formed in the rotating shaft 92, and the supply passage 92a is elongated in the axial direction. Therefore, in the swash plate compressor 90 of Patent Document 2, the physique of the swash plate compressor 90 is enlarged in the axial direction by forming the supply passage 92a.
- a supply passage 102 is formed in the rotating shaft 101, and the inside of the supply passage 102 is formed.
- An introduction hole 101 a that communicates with the outside of the rotating shaft 101 is formed.
- a suction recess 105 is formed around the rotation shaft 101, and the introduction hole 101 a can communicate with the swash plate chamber 106 and the supply passage 102 via the suction recess 105.
- Patent Document 3 when the suction recess 105 and the introduction hole 101a communicate with the swash plate chamber 106, the refrigerant in the swash plate chamber 106 is introduced from the suction recess 105 into the supply passage 102 via the introduction hole 101a. It is introduced into the cylinder bore 108 from the supply passage 102 through the rotary valve 107. Also in Patent Document 3, the introduction hole 101 a is formed in the rotation shaft 101, so that the rotation shaft 101 is elongated in the axial direction and the suction recess 105 is formed in the cylinder block 104. The physique has grown in the axial direction. Further, with respect to the supply passage 102, it is necessary to increase the diameter of the rotating shaft 101 in order to ensure the strength of the rotating shaft 101. As a result, the size of the swash plate compressor 100 has increased in the radial direction. .
- the swash plate compressors 90 and 100 adopting the conventional rotary valve use the swash plate chambers 99 and 106 as they are as the suction chambers, so that the shape of the rotary valve 107 becomes complicated and large, resulting in the swash plate compression.
- the size of the machines 90 and 100 is increased.
- An object of the present invention is to provide a compact swash plate compressor while suppressing a decrease in pulsation and suction efficiency.
- a swash plate compressor includes a cylinder block, a swash plate, a plurality of pistons, a rotating shaft, and a rotary valve.
- the cylinder block has a shaft hole, a plurality of cylinder bores, a swash plate chamber, and a suction chamber.
- the shaft hole extends through the cylinder block.
- the plurality of cylinder bores are arranged along the circumferential direction around the shaft hole.
- the suction chamber is provided between the adjacent cylinder bores so as to be isolated from the swash plate chamber.
- the swash plate is stored in the swash plate chamber.
- the plurality of pistons are moored to the swash plate and inserted into the plurality of cylinder bores, respectively.
- the rotating shaft is inserted into the shaft hole and rotates integrally with the swash plate.
- the rotary valve is provided on the rotation shaft so as to rotate integrally with the rotation shaft.
- the cylinder block includes a suction chamber communication path that communicates the suction chamber and the shaft hole, and a plurality of bore communication paths.
- the plurality of bore passages individually communicate the plurality of cylinder bores with the shaft hole.
- the rotary valve causes the suction chamber communication passage to sequentially communicate with the plurality of bore communication passages by rotating integrally with the rotary shaft.
- the suction chamber and the cylinder bore are arranged in the circumferential direction around the rotary valve.
- the size of the rotary valve in the axial direction and the radial direction, and thus the size of the swash plate compressor does not increase.
- the rotary valve is adopted as the suction method instead of the suction valve, it is possible to prevent the deterioration of the suction efficiency as compared with the suction valve.
- the suction chamber and the cylinder bore are alternately arranged in the circumferential direction around the rotary valve.
- the supply passage only needs to be formed in a shape extending in a part of the circumferential direction of the rotary valve. Therefore, the shape of the rotary valve formed on the rotating shaft can be simplified, and the length in the axial direction can be further shortened.
- the suction chamber communication passage can be formed at the same time. Therefore, there is no need to cut the suction chamber communication passage with a drill or the like after the cylinder block is cast, and the labor for manufacturing the cylinder block can be saved.
- the suction chamber communication passage is formed in an inner wall of the suction chamber and has a first recess having an opening end opened in an end surface in the axial direction of the cylinder block, and an inner wall of the shaft hole. And a second recess having an open end communicating with the swash plate chamber.
- a thrust bearing is disposed between the swash plate and the opening end of the second recess, and the thrust bearing closes the opening end of the second recess.
- the suction chamber communication path be formed at the same time, but also the opening of the suction chamber communication path and the swash plate chamber can be reduced in size, so that the thrust bearing as the closing member can be reduced in size.
- a large cylinder bore capacity can be secured in the cylinder block, and pulsation can be further reduced.
- FIG. 6 is a development view showing the rotary valve and the shaft hole in FIG. 5.
- 5A is a cross-sectional view taken along line 7a-7a in FIG. 5 showing the cylinder block of FIG. 5 from the front suction chamber side
- FIG. 5B is a line of 7b-7b in FIG. 5 showing the cylinder block from the shaft hole side.
- FIG. The fragmentary sectional view which shows the double-headed piston type swash plate type compressor of another example.
- Sectional drawing which shows the double-headed piston type swash plate type compressor of another example.
- the expanded view which shows the front side rotary valve of another example.
- FIG. The figure which shows the patent document 2.
- FIG. The figure which shows the patent document 3.
- a housing H of a double-headed piston type swash plate compressor 10 (hereinafter simply referred to as a compressor 10), of a pair of cylinder blocks 11 and 12 joined, the front side ( A front housing 13 is joined to the cylinder block 11 on the left side in FIG. 1 via a front side valve / port forming body 15.
- a rear housing 14 is joined to the cylinder block 12 on the rear side (right side in FIG. 1) via a rear side valve / port forming body 16.
- the housing H is formed with a pair of cylinder blocks 11 and 12 interposed between the front housing 13 and the rear housing 14.
- a rotary shaft 22 is inserted into the shaft holes 11a and 12a formed through the cylinder blocks 11 and 12, and the rotary shaft 22 is rotated by a seal peripheral surface formed on the inner peripheral surfaces of the shaft holes 11a and 12a. Supported as possible.
- the rotary shaft 22 is inserted so as to pass through insertion holes 15 d and 16 d formed at the center of the front side valve / port forming body 15 and the rear side valve / port forming body 16.
- insertion holes 15 d and 16 d formed at the center of the front side valve / port forming body 15 and the rear side valve / port forming body 16.
- the sealing device 23 is hermetically sealed.
- the shaft seal device 23 is accommodated in an accommodation chamber 13 c defined between the inner peripheral surface of the front housing 13
- a swash plate 24 that rotates integrally with the rotary shaft 22 is fixed to the rotary shaft 22.
- the swash plate 24 is located inside the cylinder blocks 11 and 12 and is housed in a swash plate chamber 25 defined between the cylinder blocks 11 and 12.
- a thrust bearing 26 is interposed between the end face of the front cylinder block 11 and the annular base 24 a of the swash plate 24.
- a thrust bearing 27 is interposed between the end face of the rear cylinder block 12 and the base 24 a of the swash plate 24.
- the thrust bearings 26 and 27 restrict movement of the swash plate 24 along the central axis L direction of the swash plate 24 across the swash plate 24, and the thrust bearings 26 and 27 are shaft holes in the cylinder blocks 11 and 12, respectively. It is pressed against the open end faces of 11a and 12a.
- the rear cylinder block 12 has three rear cylinder bores 29 arranged around the rotary shaft 22 so as to surround the rotary shaft 22.
- the front cylinder bore 28 and the rear cylinder bore 29 make a pair in the axial direction (front-rear direction) in which the central axis L extends, and a double-headed piston 30 as a piston is inserted into both the cylinder bores 28 and 29.
- the front side cylinder bore 28 is closed by the front side valve / port forming body 15 and the double-headed piston 30, and the rear side cylinder bore 29 is closed by the rear side valve / port forming body 16 and the double-headed piston 30.
- a front-side compression chamber 28a is defined in the front-side cylinder bore 28 by a double-headed piston 30 and a front-side valve / port forming body 15, and a double-headed piston 30 and a rear-side valve are placed in the rear-side cylinder bore 29.
- the rear compression chamber 29 a is partitioned by the port forming body 16.
- the front housing 13 and the cylinder block 11 are formed with three front side suction chambers 17 surrounding the rotary shaft 22 and penetrating the front side valve / port forming body 15. As shown in FIG. 4, the three front side suction chambers 17 are arranged one by one between the front side cylinder bores 28 adjacent in the circumferential direction around the shaft hole 11a. The three front suction chambers 17 are arranged at equal intervals on the outer peripheral side of the shaft hole 11a.
- one front side suction chamber 17 is closer to the axial direction of the rotary shaft 22 than the other two front side suction chambers 17.
- the volume increases.
- each of the three front suction chambers 17 communicates with the storage chamber 13c, and the three front suction chambers 17 communicate with each other around the storage chamber 13c. , It is a connected space.
- a front-side discharge chamber 28 b is partitioned between the front housing 13 and the front-side valve / port forming body 15 so as to surround the rotating shaft 22.
- the front discharge chamber 28 b is a space in which refrigerant from the three front compression chambers 28 a is discharged, and is annularly defined on the outer peripheral side of the front housing 13.
- this front side discharge chamber 28b a portion facing each front side compression chamber 28a through the front side valve / port forming body 15 is opened.
- the spaces facing the front-side compression chambers 28a communicate with each other through a passage, forming a continuous space.
- the cylinder block 11 has three front side discharge chambers 40 communicating with the front side discharge chamber 28b.
- the front-side discharge chamber 40 extends through the front-side valve / port forming body 15 to the front-side cylinder block 11.
- the front-side discharge chambers 40 formed at three locations are arranged around the rotating shaft 22 and are formed one by one between the front-side cylinder bores 28 adjacent to each other in the circumferential direction of the shaft hole 11a.
- Each front discharge chamber 40 is formed outside the front suction chamber 17 in the radial direction of the cylinder block 11.
- the front side valve / port forming body 15 has a discharge port 15a formed at a position corresponding to each front cylinder bore 28, and a discharge port corresponding to the discharge port 15a.
- a valve 15b is formed.
- the front side valve / port forming body 15 is formed with a retainer 15c for regulating the opening degree of the discharge valve 15b.
- the rear housing 14 and the cylinder block 12 have three rear suction chambers 18 arranged around the rotation shaft 22 (shaft hole 12a) and a rear valve / port formation. It is formed through the body 16. Similar to the front side, the three rear side suction chambers 18 are arranged one by one between the rear side cylinder bores 29 adjacent to each other in the circumferential direction of the shaft hole 12a. Of the three rear suction chambers 18, one rear suction chamber 18 is longer in the axial direction of the rotary shaft 22 than the other two rear suction chambers 18. The volume is large.
- the cylinder block 12 is integrally formed with three rear discharge chambers 42 communicating with the rear discharge chamber 29b.
- the rear side discharge chamber 42 extends from the rear housing 14 through the rear side valve / port forming body 16 to the cylinder block 12 on the rear side.
- the rear side discharge chambers 42 formed at three locations are arranged around the shaft hole 12a and are formed one by one between the rear cylinder bores 29 adjacent to each other in the circumferential direction of the shaft hole 12a.
- Each rear discharge chamber 42 is formed outside the rear suction chamber 18 in the radial direction of the cylinder block 12.
- the front-side discharge chamber 28b and the rear-side discharge chamber 29b are arranged so that one pair is formed in the front-rear direction in which the central axis L extends.
- the rear side valve / port forming body 16 has a discharge port 16a formed at a position corresponding to each rear side discharge chamber 29b, and a discharge valve 16b at a position corresponding to the discharge port 16a. Is formed. Further, the rear side valve / port forming body 16 is formed with a retainer 16c for regulating the opening degree of the discharge valve 16b.
- a suction passage 43 is formed in the cylinder blocks 11, 12.
- the suction passage 43 communicates with the front suction chamber 17 having the largest volume among the three front suction chambers 17.
- the rear-side opening communicates with the rear-side suction chamber 18 having the largest volume among the three rear-side suction chambers 18.
- a suction port 44 is formed in the front cylinder block 11.
- One end of the suction port 44 opens on the outer peripheral surface of the cylinder block 11, and the other end opens on the inner peripheral surface of the suction passage 43.
- An external pipe 32 of an external refrigerant circuit disposed outside the compressor 10 is connected to one end opening of the suction port 44.
- the suction passage 43 is formed in the cylinder blocks 11 and 12 and is isolated from the swash plate chamber 25.
- the cylinder block 11 is formed with a suction chamber communication passage 50a for communicating each front suction chamber 17 with the shaft hole 11a.
- One end of the suction chamber communication passage 50a opens to the front suction chamber 17, and the other end opens on the seal peripheral surface of the shaft hole 11a.
- the suction chamber communication passage 50 a extends while being slightly inclined along the radial direction of the cylinder block 11, and is formed in the cylinder block 11.
- the cylinder block 11 is formed with a front-bore communication passage 50b that allows the shaft hole 11a and the front-side cylinder bores 28 to communicate with each other.
- One end of the front-side bore communication passage 50 b opens on the seal circumferential surface of the shaft hole 11 a, and the other end opens on the front-side cylinder bore 28.
- the suction chamber communication passage 50a and the front bore communication passage 50b are alternately arranged in the circumferential direction of the shaft hole 11a.
- an introduction groove 22 a is formed on the front peripheral surface of the rotating shaft 22.
- the introduction groove 22a is recessed in the circumferential surface on the front housing 13 side of the rotary shaft 22 that is a solid shaft.
- the introduction groove 22a opens toward the seal peripheral surface of the shaft hole 11a, and can communicate with the suction chamber communication passage 50a and the front bore communication passage 50b individually. Then, the position of the introduction groove 22a is changed with the rotation of the rotary shaft 22, so that the suction chamber communication path 50a and the front bore communication path 50b with which the introduction groove 22a communicates are mechanically switched. It has become.
- the portion of the rotary shaft 22 surrounded by the seal peripheral surface is a front-side rotary valve RF formed integrally with the rotary shaft 22.
- the introduction groove 22a allows one suction chamber communication passage 50a and one front-side bore communication passage 50b located adjacent to each other in the circumferential direction of the shaft hole 11a to communicate with each other. Then, the rotation of the rotary shaft 22 causes the suction chamber communication passage 50a and the front bore communication passage 50b to individually communicate with each other through the introduction groove 22a, so that the front cylinder bore 28 adjacent to the front suction chamber 17 is adjacent.
- the refrigerant is inhaled. Therefore, in the present embodiment, the introduction groove 22a serves as a supply passage for communicating the front cylinder bore 28 and the front suction chamber 17 with the front rotary valve RF.
- the cylinder block 12 is formed with a rear-side introduction passage 51 for communicating each rear-side cylinder bore 29 and the shaft hole 12a.
- One end of the rear side introduction passage 51 opens to each rear side cylinder bore 29, and the other end opens on the seal peripheral surface of the shaft hole 12a.
- a supply path 22 b is formed on the peripheral surface on the rear side of the rotating shaft 22.
- One end of the supply path 22 b opens into the rear housing side suction chamber 19 in the rear housing 14.
- the other end of the rear side introduction passage 51 can communicate with the other end side of the supply passage 22b.
- the rear side introduction path 51 with which the supply path 22b communicates is mechanically switched. Therefore, the portion of the rotating shaft 22 surrounded by the seal peripheral surface is a rear-side rotary valve RR formed integrally with the rotating shaft 22.
- the introduction groove 22a is disconnected from the suction chamber communication passage 50a, the communication between the suction chamber communication passage 50a and the front bore communication passage 50b is released, and the front side
- the front side cylinder bore 28 shifts to the compression stroke and the discharge stroke.
- the refrigerant in the front side compression chamber 28a pushes the discharge valve 15b away from the discharge port 15a and is discharged into the front side discharge chamber 28b.
- the refrigerant discharged to the front discharge chamber 28b flows out from the front discharge chamber 40 through the discharge passage 45 and the discharge port 46 to the external refrigerant circuit.
- the supply passage 22b is disconnected from the rear side introduction passage 51, the communication between the rear side introduction passage 51 and the rear housing side suction chamber 19 is released, and the rear side cylinder bore 29 is When shut off, the rear cylinder bore 29 shifts to the compression stroke and the discharge stroke. Then, the refrigerant in the rear side compression chamber 29a pushes the discharge valve 16b away from the discharge port 16a and is discharged into the rear side discharge chamber 29b. Then, the refrigerant discharged to the rear side discharge chamber 29b flows out from the rear side discharge chamber 42 through the discharge passage 45 and the discharge port 46 to the external refrigerant circuit.
- the double-headed piston type swash plate compressor 10 three front side cylinder bores 28 are formed around the shaft hole 11 a in the cylinder block 11, and the front side suction chamber 17 is interposed between the adjacent front side cylinder bores 28. Were placed one by one. That is, the front cylinder bore 28 and the front suction chamber 17 are alternately arranged around the shaft hole 11a.
- the cylinder block 11 is formed with a suction chamber communication passage 50a for communicating each front suction chamber 17 and the shaft hole 11a, and a front bore communication passage 50b for communicating the front cylinder bore 28 and the shaft hole 11a.
- the suction chamber communication passage 50a and the front bore communication passage 50b are alternately arranged in the circumferential direction of the shaft hole 11a.
- each front suction chamber 17 is directly introduced into the introduction groove 22a via the suction chamber communication passage 50a in the cylinder block 11, and then the front cylinder bore 28 via the front bore communication passage 50b. Inhaled. Therefore, in order to connect the front side cylinder bore 28 and the front side suction chamber 17 adjacent to each other in the circumferential direction by the front side rotary valve RF, it is only necessary to form the introduction groove 22a in a shape extending in a part in the circumferential direction of the rotary valve RF. Good. Therefore, since the shape of the front side rotary valve RF can be simplified, the length of the front side rotary valve RF in the axial direction can be shortened.
- the size of the compressor 10 is not easily increased in size in the axial direction or the radial direction.
- a rotary valve is used instead of a suction valve, and the front side cylinder bore 28 and the front side suction chamber 17 are mechanically communicated with each other, so that deterioration of suction efficiency is prevented as compared with the suction valve. be able to.
- three front-side suction chambers 17 are formed in the cylinder block 11, a sufficient volume of the suction chamber can be secured and pulsation can be suppressed.
- One front side suction chamber 17 is formed between the front side cylinder bores 28 adjacent to each other in the circumferential direction of the shaft hole 11a.
- a suction chamber communication passage 50a is formed in the cylinder block 11 for communicating each front suction chamber 17 with the introduction groove 22a of the front rotary valve RF.
- the refrigerant in each front-side suction chamber 17 can be directly introduced into the introduction groove 22a through the suction chamber communication passage 50a. Accordingly, since it is not necessary to introduce the refrigerant into the suction pressure region of the front housing 13 once, there is no need to form the introduction groove 22 a extending from the front housing 13 to the cylinder block 11 on the rotating shaft 22. Therefore, the rotating shaft 22 is supported by the shaft hole 11a (seal peripheral surface) before and after the introduction groove 22a in the axial direction, and the bearing area of the rotating shaft 22 can be secured and the wear resistance can be improved.
- one rear side suction chamber 18 was formed between the adjacent rear side cylinder bores 29 so as to surround the rotating shaft 22. For this reason, the suction chambers 17 and 18 are provided in the radial direction of the cylinder blocks 11 and 12 on the front side and the rear side, and an increase in size of the compressor 10 in the axial direction can be suppressed.
- a front-side discharge chamber 28b is formed in the front housing 13
- a rear-side discharge chamber 29b is formed in the rear housing 14, and three front-side discharge chambers 40 communicate with the front-side discharge chamber 28b.
- Three rear discharge chambers 42 communicate with the rear discharge chamber 29b.
- Each discharge chamber 40, 42 is arranged one by one between the adjacent cylinder bores 28, 29. For this reason, in the cylinder blocks 11 and 12, the capacity
- the discharge chambers 40 and 42 are arranged outside the suction chambers 17 and 18 in the radial direction of the cylinder blocks 11 and 12. For this reason, even if the cylinder blocks 11 and 12 are thermally expanded by the high-temperature refrigerant discharged into the discharge chambers 40 and 42, the thermal expansion locations are evenly distributed in the radial direction of the cylinder blocks 11 and 12. As a result, the influence of the double-headed piston 30 due to thermal deformation of the cylinder bores 28 and 29 can be reduced.
- the discharge chambers 40 and 42 are arranged one by one between the cylinder bores 28 and 29, respectively. For this reason, even if the cylinder blocks 11 and 12 are thermally expanded by the high-temperature refrigerant discharged into the discharge chambers 40 and 42, the thermal expansion locations are evenly distributed in the circumferential direction of the cylinder blocks 11 and 12. As a result, the influence of the double-headed piston 30 due to thermal deformation of the cylinder bores 28 and 29 can be reduced.
- a suction port 44 is formed in the cylinder block 11, and a suction passage 43 communicating with the front suction chamber 17 and the rear suction chamber 18 is formed in the cylinder blocks 11 and 12. For this reason, when the refrigerant is sucked into the suction chambers 17 and 18, the refrigerant does not pass through the swash plate chamber 25. Therefore, it is possible to prevent the refrigerant sucked into the suction chambers 17 and 18 from being heated by the high-temperature blow-by gas flowing into the swash plate chamber 25 or the rotating shaft 22 heated by sliding friction.
- One front-side suction chamber 17 is formed between the front-side cylinder bores 28 adjacent in the circumferential direction so as to surround the shaft hole 11a. Further, a suction chamber communication passage 50a for communicating each front suction chamber 17 and the introduction groove 22a of the front rotary valve RF to the cylinder block 11, and a front bore for communicating the introduction groove 22a and the front cylinder bore 28. A communication passage 50b was formed. The refrigerant in each front suction chamber 17 can be sucked into the front cylinder bore 28 via the suction chamber communication passage 50a, the introduction groove 22a, and the front bore communication passage 50b. The refrigerant suction from the front suction chamber 17 to the front cylinder bore 28 can be completed.
- the contact area between the refrigerant and the introduction groove 22a can be shortened as compared with the case where the air is sucked into the front cylinder bore 28 through the groove extending into the front housing 13 and the swash plate chamber 25.
- a second recess 61 is formed corresponding to each front suction chamber 17 on the second end surface 11c which is the surface of the cylinder block 11 on the swash plate chamber 25 side in the axial direction.
- the second recess 61 is formed in the cylinder block 11 so as to extend in the radial direction from the inner wall of the shaft hole 11a.
- One end of the second recess 61 opens to the second end surface 11c of the cylinder block 11 and is connected to the opening of the shaft hole 11a.
- the other end of the second recess 61 is located in the middle of the axial length of the shaft hole 11a and does not penetrate the cylinder block 11 in the axial direction.
- the 2nd recessed part 61 is recessedly provided toward the 1st end surface 11b from the 2nd end surface 11c.
- the opening on the second end face 11 c side (swash plate chamber 25 side) in the second recess 61 is closed by the thrust bearing 26.
- the first recess 60 and the second recess 61 are connected and communicated to form a suction chamber communication passage 62.
- One end of the suction chamber communication passage 62 is formed by an opening on the front suction chamber 17 side in the first recess 60, and the other end of the suction chamber communication passage 62 is formed by an opening on the shaft hole 11 a side in the second recess 61. Is formed.
- the suction chamber communication path 62 allows the front suction chamber 17 and the introduction groove 22a to communicate with each other.
- the opening end on the swash plate chamber 25 side is closed by the thrust bearing 26, and the space between the suction chamber communication path 62 and the swash plate chamber 25 is sealed.
- the first recess 60 and the second recess 61 are formed together with the front suction chamber 17 when the cylinder block 11 is manufactured by casting.
- FIG. 6 is a diagram in which the front-side rotary valve RF is developed in the circumferential direction, and shows the peripheral surface of the front-side rotary valve RF and the shaft hole 11a through which the front-side rotary valve RF is inserted and supported by the outline shown by the solid line. .
- An introduction groove 22a is shown in these outlines.
- 6 shows a front-side bore communication passage 50b that opens to the shaft hole 11a and communicates with each front-side cylinder bore 28 by a two-dot chain line in FIG. 6, and opens to the shaft hole 11a and has each front-side suction chamber.
- 17 shows a suction chamber communication passage 62 (a region where the first concave portion 60 and the second concave portion 61 overlap with each other).
- the front-side bore communication passages 50b and the suction chamber communication passages 62 are alternately arranged along the circumferential direction of the shaft hole 11a.
- the introduction groove 22a only needs to be formed to extend partly in the circumferential direction of the rotary shaft 22. .
- the suction chamber communication passage 62 has a rectangular shape that is long in the axial direction, the suction chamber communication passage 62 and the front bore communication passage 50b can be sealed in the shaft hole 11a. They are lined up alternately in the circumferential direction. Therefore, in order to connect the front cylinder bore 28 and the front suction chamber 17 adjacent to each other in the circumferential direction by the front rotary valve RF, the front bore communication passage 50b and the suction chamber communication passage 62 adjacent to each other in the circumferential direction are provided. It is only necessary to communicate with the introduction groove 22a. Therefore, the introduction groove 22a only needs to be formed in the front-side rotary valve RF so as to extend to a part of the front-side rotary valve RF in the circumferential direction.
- the shape of the front-side rotary valve RF formed on the rotating shaft 22 can be simplified, and the length in the axial direction can be shortened. As a result, even if the front rotary valve RF is adopted as the suction method of the compressor 10 having the front suction chamber 17 in the cylinder block 11, the size does not increase in the axial direction.
- the suction chamber communication passage 62 is formed together with the front suction chamber 17 when the cylinder block 11 is cast. Therefore, compared with the case where the suction chamber communication passage 62 is cut by a drill or the like after the cylinder block 11 is cast, labor for manufacturing the cylinder block 11 can be saved.
- the suction chamber communication passage 62 is formed by connecting the first recess 60 extending from the first end surface 11b and the second recess 61 extending from the second end surface 11c. This makes it possible to reduce the opening area of the second recess 61 compared to the case where the suction chamber communication path is formed only by the second recess 61, and the opening of the second recess 61 is made by the relatively small thrust bearing 26. It can be closed.
- the suction chamber communication passage 62 is formed by connecting the first recess 60 extending from the first end surface 11b of the cylinder block 11 and the second recess 61 extending from the second end surface 11c, but the present invention is not limited thereto.
- the suction chamber communication path may be formed only by the second recess 66 extending from the second end surface 11 c of the cylinder block 11. The second recess 66 allows the front suction chamber 17 and the introduction groove 22a to communicate directly.
- a route via an in-shaft passage 65 communicating with the chamber 19 may be provided.
- the refrigerant is sucked into the front cylinder bore 28 only from the rear housing side suction chamber 19 via the in-shaft passage 65, and compared with the configuration in which the refrigerant is sucked into the front side cylinder bore 28 via the suction chamber communication passage 62.
- the diameter of the in-shaft passage 65 can be reduced. Therefore, the rotary shaft 22 and the rotary valve RF can be reduced in size in the radial direction, and the overall size of the compressor 10 can be reduced.
- the rotary valve is adopted as the suction method on the front side and the rear side, but the suction method on the rear side may be based on the suction valve instead of the rotary valve.
- the refrigerant in the rear side suction chamber 18 is collected in the rear housing side suction chamber 19 and sucked from the rear housing side suction chamber 19 into the rear side cylinder bore 29 via the rear side rotary valve RR.
- each rear side suction chamber 18 and the shaft hole 12a are individually communicated with each other through an introduction groove through a communication path, and the shaft hole 12a and the rear side cylinder bore 29 are individually communicated with each other through an introduction path.
- the refrigerant may be sucked into the rear cylinder bore 29 from the rear suction chamber 18 via the introduction groove and introduction passage of the rear rotary valve RR.
- the suction port 44 is formed in the front cylinder block 11, but the suction port 44 may be formed in another part of the housing H such as the rear cylinder block 12.
- the refrigerant that has passed through the suction port 44 is supplied to the front suction chamber 17 and the rear suction chamber 18 through the suction passage 43 formed in the cylinder blocks 11 and 12, but has passed through the suction port 44.
- the refrigerant may be supplied to the front suction chamber 17 and the rear suction chamber 18 via the swash plate chamber 25.
- three front-side discharge chambers 40 are arranged one by one between the adjacent front-side cylinder bores 28, but the front-side discharge chambers 40 may be formed in one or two places.
- a part of the introduction groove 22 a is on the front side of the rotation shaft 22 so that the suction chamber communication passage 62 always communicates with the introduction groove 22 a regardless of the rotation angle of the rotation shaft 22. It is formed in an annular shape that goes around the peripheral surface of the.
- the three rear-side discharge chambers 42 are arranged one by one between the adjacent rear-side cylinder bores 29, but the rear-side discharge chambers 42 may be formed in one or two locations.
- rear suction chambers 18 are formed, and the rear suction chambers 18 are arranged one by one between the adjacent rear cylinder bores 29.
- the rear-side suction space may be the rear housing-side suction chamber 19 alone, or the rear-side suction chamber 18 may be formed in one place or two places.
- the front suction chamber 17 communicating with the suction passage 43 has a larger volume than the other two front suction chambers 17, but the volume of the other two front suction chambers 17 is reduced to the suction passage 43. It may be larger than the volume of the front suction chamber 17 that communicates.
- the front-side suction chamber 17 communicating with the suction passage 43 is supplied with the refrigerant directly from the suction passage 43, so that the refrigerant is smoothly supplied to the front-side cylinder bore 28. Therefore, the volume is small. May be.
- the three front side suction chambers 17 may have the same volume.
- the front suction chamber 17 and the front discharge chamber 40 are formed across both the front housing 13 and the cylinder block 11, but may be formed only in the cylinder block 11.
- the rear suction chamber 18 and the rear discharge chamber 42 are formed across both the rear housing 14 and the cylinder block 12, but may be formed only in the cylinder block 12.
- the swash plate type compressor is embodied as a double-headed piston type swash plate type compressor. May be.
- RF Front rotary valve as a rotary valve
- 10 Double-head piston type swash plate compressor
- 11, 12 Cylinder block, 11a, 12a ... Shaft hole, 17 ... Front suction chamber, 18 ... Rear suction chamber, 22
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Abstract
Description
以下、本発明の斜板式圧縮機を両頭ピストン型斜板式圧縮機10に具体化した第1の実施形態を図1~図4にしたがって説明する。 (First embodiment)
A first embodiment in which the swash plate compressor of the present invention is embodied in a double-headed piston
次に、本発明を具体化した第2の実施形態を図5~図7にしたがって説明する。また、第1の実施形態と同一構成については同一符号を付すなどし、その重複する説明を省略又は簡略する。 (Second Embodiment)
Next, a second embodiment embodying the present invention will be described with reference to FIGS. In addition, the same components as those in the first embodiment are denoted by the same reference numerals, and redundant description thereof is omitted or simplified.
Claims (8)
- 軸孔と複数のシリンダボアと斜板室と吸入室とを有するシリンダブロックであって、前記軸孔は前記シリンダブロックを貫通するように延びており、前記複数のシリンダボアは前記軸孔の周りで周方向に沿って並んでおり、前記吸入室は隣り合うシリンダボアの狭間に前記斜板室から隔離して設けられる、前記シリンダブロックと、
前記斜板室に納められる斜板と、
該斜板に係留されるとともに前記複数のシリンダボアにそれぞれ挿通される複数のピストンと、
前記軸孔に挿通されるとともに前記斜板と一体回転する回転軸と、
該回転軸と一体回転するように同回転軸に設けられるロータリバルブと、を備え、
前記シリンダブロックは、前記吸入室と前記軸孔とを連通させる吸入室用連通路と、前記複数のシリンダボアをそれぞれ個別に前記軸孔と連通させる複数のボア用連通路とを有しており、
前記ロータリバルブは前記回転軸と一体回転することにより前記吸入室用連通路を前記複数のボア用連通路に順次連通させる、斜板式圧縮機。 A cylinder block having a shaft hole, a plurality of cylinder bores, a swash plate chamber, and a suction chamber, the shaft hole extending through the cylinder block, and the plurality of cylinder bores circumferentially around the shaft hole The cylinder block, the suction chamber is provided separately from the swash plate chamber between the adjacent cylinder bores, and
A swash plate housed in the swash plate chamber;
A plurality of pistons moored to the swash plate and respectively inserted into the plurality of cylinder bores;
A rotating shaft that is inserted through the shaft hole and rotates integrally with the swash plate;
A rotary valve provided on the rotary shaft so as to rotate integrally with the rotary shaft,
The cylinder block has a suction chamber communication path that communicates the suction chamber and the shaft hole, and a plurality of bore communication paths that individually communicate the plurality of cylinder bores with the shaft hole,
The rotary valve is a swash plate type compressor that causes the suction chamber communication passage to sequentially communicate with the plurality of bore communication passages by rotating integrally with the rotary shaft. - 前記吸入室は、隣り合うシリンダボアの狭間にそれぞれ位置する複数の吸入室を含み、
前記吸入室用連通路は、前記複数の吸入室をそれぞれ個別に前記軸孔と連通させる複数の吸入室用連通路を含む、請求項1に記載の斜板式圧縮機。 The suction chamber includes a plurality of suction chambers respectively positioned between adjacent cylinder bores,
2. The swash plate compressor according to claim 1, wherein the suction chamber communication path includes a plurality of suction chamber communication paths that individually communicate the plurality of suction chambers with the shaft hole. - 前記シリンダブロックは、隣り合うシリンダボアの狭間にそれぞれ位置する複数の吐出室を有する、請求項2に記載の斜板式圧縮機。 The swash plate compressor according to claim 2, wherein the cylinder block has a plurality of discharge chambers respectively located between adjacent cylinder bores.
- 前記複数の吐出室は、前記シリンダブロックの径方向において、前記吸入室の外側に配置されている請求項3に記載の斜板式圧縮機。 The swash plate compressor according to claim 3, wherein the plurality of discharge chambers are arranged outside the suction chamber in a radial direction of the cylinder block.
- 前記シリンダブロックは、外部配管が接続される吸入口と、該吸入口と前記吸入室とを連通する吸入通路とを有し、
前記吸入通路は前記斜板室から隔離して設けられる、請求項1~請求項4のうちいずれか一項に記載の斜板式圧縮機。 The cylinder block has a suction port to which an external pipe is connected, and a suction passage that communicates the suction port and the suction chamber.
The swash plate compressor according to any one of claims 1 to 4, wherein the suction passage is provided separately from the swash plate chamber. - 前記吸入室用連通路は、前記軸孔の内壁に形成された凹部によって構成され、同凹部は前記斜板室に連通する開口端を有し、
前記斜板と前記凹部の開口端との間にはスラストベアリングが配置され、
前記スラストベアリングは前記凹部の開口端を閉塞する、請求項1~請求項5のうちのいずれか一項に記載の斜板式圧縮機。 The suction chamber communication passage is constituted by a recess formed in the inner wall of the shaft hole, and the recess has an open end communicating with the swash plate chamber,
A thrust bearing is disposed between the swash plate and the opening end of the recess,
The swash plate compressor according to any one of claims 1 to 5, wherein the thrust bearing closes an opening end of the recess. - 前記吸入室用連通路は、前記吸入室の内壁に形成されるとともに前記シリンダブロックの軸方向における端面に開口する開口端を有する第1凹部と、前記軸孔の内壁に形成されるとともに前記斜板室に連通する開口端を有する第2凹部とによって構成され、
前記斜板と前記第2凹部の開口端との間にはスラストベアリングが配置され、
前記スラストベアリングは前記第2凹部の開口端を閉塞する、請求項1~請求項5のうちいずれか一項に記載の斜板式圧縮機。 The suction chamber communication passage is formed in the inner wall of the suction chamber and has a first recess having an opening end that opens at an end surface in the axial direction of the cylinder block, and is formed in the inner wall of the shaft hole and the inclined wall. A second recess having an open end communicating with the plate chamber,
A thrust bearing is disposed between the swash plate and the open end of the second recess,
The swash plate compressor according to any one of claims 1 to 5, wherein the thrust bearing closes an opening end of the second recess. - 前記複数のシリンダボアは3つのシリンダボアである、請求項1~請求項7のうちいずれか一項に記載の斜板式圧縮機。 The swash plate compressor according to any one of claims 1 to 7, wherein the plurality of cylinder bores are three cylinder bores.
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN2012800149814A CN103459846A (en) | 2011-03-31 | 2012-03-29 | Swash-plate-type compressor |
JP2013507731A JP5574041B2 (en) | 2011-03-31 | 2012-03-29 | Swash plate compressor |
BR112013025034A BR112013025034A2 (en) | 2011-03-31 | 2012-03-29 | oscillating plate type compressor |
KR1020137025362A KR101450596B1 (en) | 2011-03-31 | 2012-03-29 | Swash-plate-type compressor |
US14/002,801 US20130343922A1 (en) | 2011-03-31 | 2012-03-29 | Swash-plate-type compressor |
Applications Claiming Priority (2)
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JP2011-079843 | 2011-03-31 | ||
JP2011079843 | 2011-03-31 |
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WO2012133669A1 true WO2012133669A1 (en) | 2012-10-04 |
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PCT/JP2012/058407 WO2012133669A1 (en) | 2011-03-31 | 2012-03-29 | Swash-plate-type compressor |
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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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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 |
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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 |
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JPS5849433Y2 (en) * | 1978-10-16 | 1983-11-11 | 株式会社ボッシュオートモーティブ システム | Rotating swash plate compressor |
JP2616295B2 (en) * | 1991-09-02 | 1997-06-04 | 株式会社豊田自動織機製作所 | Swash plate compressor for refrigeration equipment |
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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 |
JP4946340B2 (en) * | 2005-10-17 | 2012-06-06 | 株式会社豊田自動織機 | Double-head piston compressor |
JP4702145B2 (en) | 2006-03-31 | 2011-06-15 | 株式会社豊田自動織機 | Swash plate compressor |
JP5045555B2 (en) * | 2008-05-29 | 2012-10-10 | 株式会社豊田自動織機 | Double-head piston type swash plate compressor |
JP2010013987A (en) * | 2008-07-02 | 2010-01-21 | Toyota Industries Corp | Refrigerant suction structure in piston type 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 JP JP2013507731A patent/JP5574041B2/en not_active Expired - Fee Related
- 2012-03-29 BR BR112013025034A patent/BR112013025034A2/en not_active IP Right Cessation
- 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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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 |
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KR20130131450A (en) | 2013-12-03 |
CN103459846A (en) | 2013-12-18 |
BR112013025034A2 (en) | 2016-12-27 |
KR101450596B1 (en) | 2014-10-14 |
JP5574041B2 (en) | 2014-08-20 |
JPWO2012133669A1 (en) | 2014-07-28 |
US20130343922A1 (en) | 2013-12-26 |
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