WO2020196577A1 - ピストン式圧縮機 - Google Patents
ピストン式圧縮機 Download PDFInfo
- Publication number
- WO2020196577A1 WO2020196577A1 PCT/JP2020/013192 JP2020013192W WO2020196577A1 WO 2020196577 A1 WO2020196577 A1 WO 2020196577A1 JP 2020013192 W JP2020013192 W JP 2020013192W WO 2020196577 A1 WO2020196577 A1 WO 2020196577A1
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- WIPO (PCT)
- Prior art keywords
- passage
- chamber
- drive shaft
- suction
- moving body
- 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
- F04B27/10—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
- F04B27/12—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 having plural sets of cylinders or pistons
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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
- F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
- F04B27/0878—Pistons
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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
- F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
- F04B27/0895—Component parts, e.g. sealings; Manufacturing or assembly thereof driving means
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1045—Cylinders
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1054—Actuating elements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1081—Casings, housings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/10—Adaptations or arrangements of distribution members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2210/00—Working fluid
- F05B2210/10—Kind or type
- F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
Definitions
- This disclosure relates to a piston type compressor.
- Patent Document 1 discloses a conventional piston type compressor (hereinafter, simply referred to as a compressor).
- the compressor includes a housing, a drive shaft, a fixed swash plate, a piston, a suction passage, a discharge valve, a moving body, and a control valve.
- the housing has a first housing and a cylinder block.
- the first housing is joined to the cylinder block in the axial direction of the drive shaft via a discharge valve.
- a discharge chamber and a control pressure chamber are formed in the first housing.
- the cylinder block is formed with a first connecting passage that communicates with the cylinder bores.
- a suction region is formed in the cylinder block. The suction region has a lower pressure than the discharge chamber.
- the suction area is specifically a swash plate chamber that rotatably accommodates the swash plate.
- a shaft hole is formed in the cylinder block. The shaft hole extends in the axial direction and is connected to the control pressure chamber.
- the drive shaft is rotatably supported in the shaft hole.
- the fixed swash plate can be rotated in the swash plate chamber by the rotation of the drive shaft, and the inclination angle with respect to the plane perpendicular to the drive shaft is constant.
- the piston forms a compression chamber in the cylinder bore and is connected to a fixed swash plate.
- the discharge valve is located between the compression chamber and the discharge chamber, and discharges the refrigerant in the compression chamber to the discharge chamber.
- the control pressure chamber is a control pressure.
- the suction passage is formed on the drive shaft.
- the suction passage has an axial path extending in the axial direction in the drive shaft and a radial path extending in the radial direction of the drive shaft and connecting the swash plate chamber and the axial path via a fixed swash plate.
- the moving body is provided on the drive shaft and is located in the shaft hole and in the control pressure chamber. The moving body can rotate around the axis integrally with the drive shaft, and can move in the axial direction with respect to the drive shaft.
- a second passage is formed in the moving body. The second passage communicates with the suction passage and intermittently communicates with the first passage as the drive shaft rotates.
- the moving body is provided with a sealing member. The sealing member is located between the outer peripheral surface of the drive shaft and the inner wall surface of the control pressure chamber. The control valve controls the control pressure.
- the suction region and the control pressure chamber are sealed by a sealing member. Then, in this compressor, the refrigerant flows from the swash plate chamber into the shaft path by the route, and the refrigerant in the shaft path is sucked into the compression chamber by the second passage and the first passage. Further, the moving body changes its position in the axial direction with respect to the drive shaft based on the control pressure. As a result, in this compressor, the communication area between the first passage and the second passage per rotation of the drive shaft changes. In this way, in this compressor, it is possible to change the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber.
- the piston type compressor of the present disclosure has a cylinder block in which a plurality of cylinder bores are formed, and has a housing in which a shaft hole, a discharge chamber, and a suction region having a lower pressure than the discharge chamber are formed.
- a drive shaft rotatably supported in the shaft hole and A fixed swash plate that can be rotated in the housing by rotation of the drive shaft and has a constant inclination angle with respect to a plane perpendicular to the drive shaft.
- a piston that forms a compression chamber in each cylinder bore and is connected to the fixed swash plate, A suction passage for sucking the refrigerant in the suction region into the compression chamber, A discharge valve that discharges the refrigerant in the compression chamber to the discharge chamber, A moving body provided on the drive shaft, located in the shaft hole, rotating integrally with the drive shaft, and movable with respect to the drive shaft in the axial direction of the drive shaft based on a control pressure. , A control valve for controlling the control pressure is provided.
- the cylinder block is formed with a first passage that communicates with the cylinder bore.
- the moving body is formed with a second passage that intermittently communicates with the first passage as the drive shaft rotates.
- a piston-type compressor in which the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber changes according to the position of the moving body in the axial direction.
- the shaft hole has an inner wall surface through which the first continuous passage opens.
- the housing is arranged on one side of the drive shaft in the axial direction, the discharge chamber and the control pressure chamber are formed, and the housing is joined to the cylinder block in the axial direction via the discharge valve.
- the cylinder block has an extending portion extending into the control pressure chamber in the axial direction and a part of the shaft hole is formed.
- the suction passage has a first suction passage formed on the drive shaft.
- the first suction passage extends in the drive shaft in the axial direction, communicates with the second communication passage, and communicates with the control pressure chamber, and extends in the radial direction of the drive shaft, and the oblique direction. It has a path that connects the board chamber and the shaft path.
- the moving body is located in the axial path in connection with the first moving body in which the second continuous passage is formed and the first moving body, and faces the control pressure chamber in the axial path. It has a second moving body that can move in the axial direction.
- the drive shaft is formed in an annular shape and is located in the extending portion, and the inner wall surface is slid around the shaft center by the drive shaft that rotates around the shaft center, while the suction region and the control pressure are formed.
- a first sealing member is provided to seal the space between the chamber and the chamber.
- a holding groove formed in an annular shape, located in the extending portion, and accommodating and holding the first sealing member is formed.
- the holding groove is arranged on the control pressure chamber side with respect to the discharge valve in the axial direction.
- a first sealing member is provided on the drive shaft, and the suction region and the control pressure chamber are sealed by this first sealing member.
- the drive shaft rotates around the axis in a state of being supported by the shaft hole, but does not move in the direction of the axis. Therefore, although the first sealing member slides the inner wall surface of the shaft hole around the shaft center by the drive shaft rotating around the shaft center, the inner wall surface of the shaft hole does not slide in the axial direction. ..
- the first sealing member is less likely to be worn, and the first sealing member can suitably prevent leakage of the refrigerant between the suction region and the control pressure chamber.
- the first sealing member is located in the extending portion by being housed in the holding groove formed on the outer peripheral surface of the drive shaft.
- the control pressure of the control pressure chamber is likely to act. Therefore, the first sealing member is easily pressed against the holding groove in the axial direction by the control pressure, and in this respect as well, in this compressor, the suction region and the control pressure chamber are provided by the first sealing member. The space between them can be suitably sealed.
- the holding groove is arranged on the control pressure chamber side with respect to the discharge valve in the axial direction. Therefore, the holding groove and the first sealing member housed in the holding groove are arranged at a position away from the compression chamber and the first continuous passage. Therefore, in this compressor, even if a part of the high-pressure refrigerant flows through the first passage and flows into the shaft hole, the high-pressure refrigerant is first sealed with the holding groove and the holding groove. It is possible to prevent it from flowing to another compression chamber or to a control pressure chamber via a stop member.
- control pressure in the control pressure chamber can be suitably adjusted, and the moving body can be suitably moved in the axial direction with respect to the drive shaft based on the control pressure.
- the piston type compressor of the present disclosure has excellent durability and exhibits high controllability.
- the suction passage has a second suction passage formed in the cylinder block, and one end of the second suction passage opens to the suction region and the other end communicates with the second passage. It is preferable that the inner wall surface is opened as much as possible.
- the refrigerant in the suction region is sucked into the compression chamber through the first suction passage, the second passage, and the first passage.
- the second suction passage communicates with the second continuous passage, the refrigerant in the suction region is also sucked into the compression chamber by the second suction passage.
- the flow rate of the refrigerant sucked from the suction region into the compression chamber can be sufficiently secured, so that the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber can be suitably increased. ..
- this compressor since the flow rate of the refrigerant sucked from the suction region into the compression chamber can be sufficiently secured by the first suction passage and the second suction passage, only the first suction passage or the second suction passage is used. Unlike the case where the flow rate of the refrigerant sucked into the compression chamber is secured, it is not necessary to make the first suction passage and the second suction passage excessively large. Therefore, in this compressor, it is possible to suppress the increase in size of the drive shaft and the size of the cylinder block.
- this compressor can suppress the increase in size while exhibiting high performance.
- the suction area can be a swash plate chamber that rotatably accommodates a fixed swash plate.
- the swash plate chamber also serves as a suction area, it is not necessary to provide a dedicated space as a suction area for the housing. Therefore, it is possible to reduce the size of the housing and the compressor while facilitating the manufacturing. Further, the refrigerant in the swash plate chamber can be suitably sucked into the compression chamber through the first suction passage and the second suction passage.
- the cylinder bore may consist of a one-sided cylinder bore arranged on one side in the axial direction and a other-side cylinder bore arranged on the other side in the axial direction.
- the shaft hole may have one side shaft hole arranged on one side in the axial direction and the other side shaft hole arranged on the other side in the axial direction.
- the piston may have a one-sided head that forms a one-sided compression chamber in the one-sided cylinder bore and a other-sided head that forms the other-side compression chamber in the other-side cylinder bore.
- the first communication passage may consist of a one-sided first passage that communicates with the one-side cylinder bore and a other-side first passage that communicates with the other cylinder bore.
- the one-side shaft hole may have a one-side inner wall surface through which the one-side first communication passage opens.
- the other side shaft hole may have the other side inner wall surface through which the other side first continuous passage opens.
- the second passage can communicate with the first passage on one side.
- the first suction passage may have a connecting path extending in the radial direction of the drive shaft and communicating the shaft path and the first communication path on the other side.
- the second suction passage has a second suction passage on one side that opens into the swash plate chamber on one end side and opens on the inner wall surface on one side so that the other side can communicate with the second communication passage, and the other side that allows communication with the connecting passage on one end side.
- the first sealing member preferably slides on the inner wall surface on one side around the axis.
- the refrigerant in the swash plate chamber is sucked into the one-side compression chamber via the first suction passage, the second passage, and the one-side first passage, and the first suction passage and the other-side first passage. Is sucked into the compression chamber on the other side. Further, if the second suction passage on one side communicates with the second continuous passage, the refrigerant in the swash plate chamber is sucked into the compression chamber on one side by the second suction passage on one side. Further, if the second suction passage on the other side communicates with the connecting path, the refrigerant in the swash plate chamber is sucked into the compression chamber on the other side by the second suction passage on the other side. As a result, in this compressor, it is possible to sufficiently secure the flow rates of the refrigerant sucked from the swash plate chamber into the one-side compression chamber and the other-side compression chamber, respectively.
- the drive shaft may be formed with a guide window that communicates with the shaft path and opens in the shaft hole on one side to which the first moving body is arranged.
- the first moving body may communicate the first passage and the second passage on one side.
- the drive shaft may make the first passage and the second passage on one side non-communication. Then, the second moving body is located in the axial path, and the flow rate of the refrigerant discharged from the one-side compression chamber to the discharge chamber is reduced, and the second moving body is sucked from the swash plate chamber into the other-side compression chamber by the first suction passage. It is preferable that a suction valve body that reduces the flow rate of the refrigerant is connected.
- the drive shaft makes the first passage and the second passage on one side non-communication, the load due to the high-pressure refrigerant from the compression chamber on one side in the compression stroke and the discharge stroke (hereinafter referred to as compression load). Acts on the drive shaft through the first passage on one side. As a result, the drive shaft receives the compressive load, so that the compressive load is unlikely to act on the first moving body. Therefore, the first moving body, and thus the moving body, easily moves in the axial direction due to the control pressure.
- the suction valve body sucks the refrigerant from the swash plate chamber into the other-side compression chamber by the first suction passage. Reduce the flow rate. That is, in this compressor, the flow rate of the refrigerant discharged from the one-side compression chamber to the discharge chamber is reduced, so that the flow rate of the refrigerant discharged from the other-side compression chamber to the discharge chamber is also reduced. In this way, in this compressor, the flow rate of the refrigerant discharged to the discharge chamber can be changed as the entire compression chamber including the one-side compression chamber and the other-side compression chamber.
- the second moving body may be provided with a second sealing member that seals between the swash plate chamber and the control pressure chamber. Then, the second sealing member is located closer to the guide window than the first sealing member in the axial direction when the flow rate of the refrigerant discharged from the one-side compression chamber to the discharge chamber is maximum. Is preferable.
- the second sealing member can also seal between the swash plate chamber and the control pressure chamber, that is, between the suction region and the control pressure chamber.
- the second moving body moves in the axial direction in the axial direction, it does not rotate relative to the drive shaft around the axial center. Therefore, although the second sealing member slides in the axial direction in the axial direction with the movement of the second moving body, the second sealing member does not slide around the axial center in the axial path. Therefore, the second sealing member is also less likely to be worn, and the second sealing member can suitably prevent the refrigerant from leaking between the swash plate chamber and the control pressure chamber through the shaft path.
- the second sealing member is located at a position farther from the guide window than the first sealing member in the axial direction.
- the second moving body needs to be enlarged in the axial direction
- the drive shaft also needs to be enlarged in the axial direction in order to secure the axial movement of the second moving body in the axial path.
- the second sealing member is closer to the guide window than the first sealing member in the axial direction when the flow rate of the refrigerant discharged from the one-side compression chamber to the discharge chamber is maximum. Located on the near side.
- the second moving body can be miniaturized in the axial direction, and as a result, the drive shaft can be miniaturized in the axial direction.
- each one-sided first passage may be arranged in the circumferential direction with respect to the cylinder block. Further, the circumferential distance between the first passages on each one side may gradually decrease from the cylinder side on one side toward the inner wall surface side on one side. The distance in the axial direction from each one-sided first communication passage to the first sealing member in the one-side shaft hole is preferably longer than the minimum circumferential distance between each one-side first communication passage. ..
- the first sealing member can be sufficiently separated from the first passage on each one side in the axial direction, and the first sealing member can be brought closer to the control pressure chamber in the axial direction by that amount. Therefore, the first sealing member can be suitably pressed against the holding groove in the axial direction by the control pressure, and the suction region and the control pressure chamber can be more preferably sealed by the first sealing member. Further, by moving the first sealing member away from the first passage on each side in the axial direction, the holding groove can also be sufficiently kept away from the first passage on each side in the axial direction. Therefore, in this compressor, it is preferable that the high-pressure refrigerant flows through the holding groove or holding groove and the first sealing member to another compression chamber or to the control pressure chamber. Can be prevented.
- the piston type compressor of the present disclosure has excellent durability and exhibits high controllability.
- FIG. 1 is a cross-sectional view of the piston type compressor of the first embodiment at the minimum flow rate.
- FIG. 2 is a cross-sectional view of the piston type compressor of the first embodiment at the maximum flow rate.
- FIG. 3 is an enlarged cross-sectional view of a main part showing the AA cross section of FIG. 1 related to the piston type compressor of the first embodiment.
- FIG. 4 is an enlarged cross-sectional view of a main part showing a BB cross section of FIG. 1 according to the piston type compressor of the first embodiment.
- FIG. 5 is an enlarged cross-sectional view of a main part showing a BB cross section of FIG. 1 according to the piston type compressor of the first embodiment.
- FIG. 6 is an enlarged cross-sectional view of a main part similar to FIG.
- FIG. 7 is an enlarged cross-sectional view of a main part showing a CC cross section of FIG. 2 related to the piston type compressor of the first embodiment.
- FIG. 8 is an exploded view showing a drive shaft, a moving body, a suction valve body, and the like, which are related to the piston type compressor of the first embodiment.
- FIG. 9 is an enlarged cross-sectional view of a main part showing a drive shaft related to the piston type compressor of the first embodiment.
- FIG. 10 is an enlarged cross-sectional view showing a DD cross section of FIG. 8 related to the piston type compressor of the first embodiment.
- FIG. 11 is an enlarged cross-sectional view of a main part showing a moving body and the like at the minimum flow rate according to the piston type compressor of the first embodiment.
- FIG. 12 is an enlarged cross-sectional view of a main part showing a moving body or the like that is related to the piston type compressor of the first embodiment and has moved forward from the minimum flow rate.
- FIG. 13 is an enlarged cross-sectional view of a main part showing a moving body and the like at the maximum flow rate according to the piston type compressor of the first embodiment.
- FIG. 14 is an enlarged cross-sectional view of a main part of the piston type compressor of the first embodiment, showing a suction valve body and the like at the minimum flow rate.
- FIG. 15 is an enlarged cross-sectional view of a main part of the piston type compressor of the first embodiment, showing a suction valve body and the like at the maximum flow rate.
- FIG. 16 is an enlarged cross-sectional view of a main part similar to FIG. 11 showing a moving body and the like at the minimum flow rate, relating to the piston type compressor of the second embodiment.
- the compressor of the first embodiment includes a housing 1, a drive shaft 3, a fixed swash plate 5, a plurality of pistons 7, a first valve forming plate 8, and a second valve. It includes a forming plate 9, a moving body 11, a suction passage 12, and a control valve 15.
- the first and second valve forming plates 8 and 9 are examples of the "discharge valve" in the present disclosure.
- the housing 1 has a front housing 17, a rear housing 19, a first cylinder block 21, and a second cylinder block 22.
- the first and second cylinder blocks 21 and 22 are examples of the "cylinder block” in the present disclosure.
- the rear housing 19 is an example of the "first housing” in the present disclosure.
- the side where the front housing 17 is located is the front side of the compressor
- the side where the rear housing 19 is located is the rear side of the compressor
- the front-rear direction of the compressor is defined.
- the vertical direction of the compressor is defined with the upper side of the paper surface of FIGS. 1 and 2 as the upper side of the compressor and the lower side of the paper surface as the lower side of the compressor.
- FIGS. 3 and 3 the front-back direction and the up-down direction are displayed corresponding to FIGS. 1 and 2.
- the front-rear direction and the like in the embodiment are examples, and the posture of the compressor of the present disclosure is appropriately changed according to the vehicle to be mounted.
- the front housing 17 has a front wall 17a extending in the radial direction and a peripheral wall 17b integrally with the front wall 17a and extending rearward from the front wall 17a in the axial direction O direction of the drive shaft 3, and is substantially cylindrical. It is in the shape.
- the axis O extends parallel to the front-rear direction of the compressor.
- a first discharge chamber 27 is formed in the front housing 17.
- the first discharge chamber 27 is formed in an annular shape.
- a first boss portion 171 and a first shaft hole 173 are formed on the front wall 17a.
- the first boss portion 171 projects forward in the O direction of the axial center.
- the first shaft hole 173 penetrates the front wall 17a in the axial center O direction.
- a shaft sealing device 16 is provided in the first shaft hole 173.
- a control pressure chamber 28 and a second discharge chamber 29 are formed in the rear housing 19.
- the control pressure chamber 28 is located on the central side of the rear housing 19.
- the second discharge chamber 29 is formed in an annular shape and is located on the outer peripheral side of the control pressure chamber 28.
- the first cylinder block 21 is located between the front housing 17 and the second cylinder block 22.
- the first cylinder block 21 is formed with a first recess 210, a suction port 211, a first discharge passage 212, and a discharge port 213.
- the first recess 210 is recessed from the rear end of the first cylinder block 21 toward the front.
- the suction port 211 communicates with the first recess 210, extends in the radial direction of the first cylinder block 21, and opens to the outside of the first cylinder block 21.
- the suction port 211 is connected to the evaporator via a pipe.
- the first discharge passage 212 extends linearly in the axial center O direction and penetrates the first cylinder block 21.
- the discharge port 213 communicates with the first discharge passage 212, extends in the radial direction of the first cylinder block 21, and opens to the outside of the first cylinder block 21.
- the discharge port 213 is connected to the condenser via a pipe.
- the piping, evaporator and condenser are not shown.
- the first cylinder block 21 is formed with the first cylinder bores 21a to 21e, the second shaft hole 23, and the front side passages 24a to 24e. ..
- the first cylinder bores 21a to 21e are an example of the "other side cylinder bore” in the present disclosure.
- the second shaft hole 23 is an example of the “other side shaft hole” in the present disclosure.
- the front side passages 24a to 24e are examples of the "other side first passage” in the present disclosure.
- the first cylinder bores 21a to 21e are arranged at equal angular intervals in the circumferential direction. As shown in FIGS. 1 and 2, each of the first cylinder bores 21a to 21e extends linearly in the axis O direction in the first cylinder block 21 and penetrates the first cylinder block 21. The number of first cylinder bores 21a to 21e can be appropriately designed.
- the second shaft hole 23 is located on the center side of the first cylinder block 21.
- the second shaft hole 23 extends linearly in the axis O direction in the first cylinder block 21 and penetrates the first cylinder block 21.
- the second shaft hole 23 has an inner wall surface 231.
- the inner wall surface 231 is an example of the “other side inner wall surface” in the present disclosure.
- the front side passages 24a to 24e are located between the first cylinder bores 21a to 21e and the second shaft hole 23.
- the front side passages 24a to 24e extend in the radial direction of the first cylinder block 21 from the second shaft hole 23 side toward the first cylinder bores 21a to 21e.
- the ends of the front side passages 24a to 24e on the first cylinder bores 21a to 21e side are opened in the first cylinder bores 21a to 21e.
- the ends of the front side passages 24a to 24e on the second shaft hole 23 side are open to the inner wall surface 231 of the second shaft hole 23. In this way, the front side communication passages 24a to 24e communicate with the first cylinder bores 21a to 21e and the second shaft hole 23.
- front side suction passages 61a to 61e are formed in the first cylinder block 21.
- the front side suction passages 61a to 61e are examples of the "other side second suction passage" in the present disclosure.
- the front side suction passages 61a to 61e are located between the first cylinder bores 21a to 21e and the second shaft hole 23, and are arranged at different positions from the front side communication passages 24a to 24e.
- the front intake passages 61a to 61e extend from the front side to the rear side in the first cylinder block 21. Further, the front suction passages 61a to 61e extend away from the second shaft hole 23 in the radial direction of the first cylinder block 21 from the front side to the rear side. As a result, as shown in FIG. 3, each front end of the front side suction passages 61a to 61e is opened in the inner wall surface 231 of the second shaft hole 23 at a position different from that of the front side continuous passages 24a to 24e. Further, as shown in FIGS. 1 and 2, each rear end of the front side suction passages 61a to 61e is open to the first recess 210.
- the shape and number of the front suction passages 61a to 61e can be appropriately designed. Further, in FIG. 3, in order to facilitate the explanation, the shapes of the front side suction passages 61a to 61e are shown in a simplified manner.
- the second cylinder block 22 is located between the first cylinder block 21 and the rear housing 19.
- a second recess 220 and a second discharge passage 221 are formed in the second cylinder block 22.
- the second recess 220 is recessed from the front end of the second cylinder block 22 toward the rear.
- the second discharge passage 221 extends linearly in the axial center O direction and penetrates the second cylinder block 22.
- the suction port 211 and the discharge port 213 may be formed on the second cylinder block 22.
- the second cylinder block 22 is formed with the second cylinder bores 22a to 22e, and the third shaft hole 25 and the rear side passages 26a to 26e are formed.
- the second cylinder bores 22a to 22e are an example of the "one-sided cylinder bore” in the present disclosure.
- the third shaft hole 25 is an example of the "one-sided shaft hole” in the present disclosure.
- the rear side passages 26a to 26e are examples of the "one-sided first passage” in the present disclosure.
- the "shaft hole” in the present disclosure is configured by the first shaft hole 173, the second shaft hole 23, and the third shaft hole 25 shown in FIGS. 1 and 2.
- the second cylinder bores 22a to 22e are arranged at equal angular intervals in the circumferential direction. As shown in FIGS. 1 and 2, the second cylinder bores 22a to 22e each extend linearly in the second cylinder block 22 in the axial direction O direction and penetrate the second cylinder block 22.
- the inner diameters of the second cylinder bores 22a to 22e are the same as the inner diameters of the first cylinder bores 21a to 21e, respectively.
- the number of the second cylinder bores 22a to 22e can be appropriately designed according to the number of the first cylinder bores 21a to 21e. Further, the inner diameters of the first cylinder bores 21a to 21e and the inner diameters of the second cylinder bores 22a to 22e may be designed to be different from each other.
- the third shaft hole 25 is located on the center side of the second cylinder block 22.
- the third shaft hole 25 extends linearly in the axis O direction in the second cylinder block 22 and penetrates the second cylinder block 22.
- the third shaft hole 25 has the same diameter as the second shaft hole 23.
- the third shaft hole 25 has an inner wall surface 251.
- the inner wall surface 251 is an example of the “one-sided inner wall surface” in the present disclosure.
- the rear side passages 26a to 26e are located between the second cylinder bores 22a to 22e and the third shaft hole 25.
- the rear side passages 26a to 26e extend in the radial direction of the second cylinder block 22 from the third shaft hole 25 side toward the second cylinder bores 22a to 22e.
- the ends of the rear side passages 26a to 26e on the second cylinder bores 22a to 22e side are opened in the second cylinder bores 22a to 22e.
- the ends of the rear side passages 26a to 26e on the third shaft hole 25 side are open to the inner wall surface 251 of the third shaft hole 25. In this way, the rear side communication passages 26a to 26e communicate with the second cylinder bores 22a to 22e and the third shaft hole 25.
- the rear side passages 26a to 26e extend radially from the third shaft hole 25 side toward the second cylinder bores 22a to 22e. Therefore, the circumferential distance between the rear side passages 26a to 26e gradually decreases from the second cylinder bores 22a to 22e side toward the third shaft hole 25 side.
- the distance between the rear side passage 26a and the rear side passage 26e in the circumferential direction is the first. The maximum distance is obtained at the ends of the two cylinder bores 22a and 22e. Then, the minimum distance is reached at the end of the third shaft hole 25 side.
- the maximum distance between the rear side passages 26a to 26e in the circumferential direction is the first length L1
- the minimum distance between the rear side passages 26a to 26e in the circumferential direction is the second length L2.
- rear suction passages 63a to 63e are formed in the second cylinder block 22.
- the rear side suction passages 63a to 63e are examples of the "one side second suction passage" in the present disclosure.
- the rear side suction passages 63a to 63e are arranged between the second cylinder bores 22a to 22e and the third shaft hole 25 at different positions from the rear side continuous passages 26a to 26e.
- the rear suction passages 63a to 63e extend from the front side to the rear side in the second cylinder block 22. Further, the rear suction passages 63a to 63e extend so as to approach the third shaft hole 25 in the radial direction of the second cylinder block 22 from the front side to the rear side. As a result, the front ends of the rear suction passages 63a to 63e are opened in the second recess 220. Then, as shown in FIGS. 4 to 6, each rear end of the rear side suction passages 63a to 63e is opened in the inner wall surface 251 of the third shaft hole 25 at a position different from that of the rear side continuous passages 26a to 26e. There is.
- the shape and number of the rear intake passages 63a to 63e can be appropriately designed. Further, in FIGS. 4 to 7, in order to facilitate the explanation, the rear intake passages 63a to 63e are illustrated by virtual lines, and the shapes of the rear intake passages 63a to 63e are simplified and illustrated. ..
- the second cylinder block 22 has a support protrusion 240.
- the support protrusion 240 is an example of the "extending portion" in the present disclosure.
- the support protrusion 240 is integrally formed with the second cylinder block 22.
- the support projection 240 is located on the rear side of the second cylinder block 22 in the axial O direction, that is, the control pressure, with respect to the second cylinder bores 22a to 22e and the rear side passages 26a to 26e. It extends toward the chamber 28 side.
- the support protrusion 240 is formed to have substantially the same diameter as the inner diameter of the control pressure chamber 28.
- the support protrusion 240 has a tubular shape, and a part of the third shaft hole 25 is formed inside. In other words, the third shaft hole 25 extends to the inside of the support protrusion 240, and the inner wall surface 251 extends to the inside of the support protrusion 240.
- a gasket 20 is provided between the first cylinder block 21 and the second cylinder block 22.
- the first cylinder block 21 and the second cylinder block 22 are joined in a state where the first recess 210 and the second recess 220 face each other.
- the first recess 210 and the second recess 220 form a swash plate chamber 31 between the first cylinder block 21 and the second cylinder block 22, and thus in the housing 1.
- Low-pressure refrigerant gas that has passed through the evaporator is sucked into the swash plate chamber 31 by the suction port 211.
- the swash plate chamber 31 has a suction pressure, which is lower than that of the first and second discharge chambers 27 and 29. That is, in this compressor, the swash plate chamber 31 is the "suction area" in the present disclosure.
- the rear ends of the front suction passages 61a to 61e are open to the first recess 210, and the front ends of the rear suction passages 63a to 63e are open to the second recess 220. Therefore, the rear ends of the front side suction passages 61a to 61e and the front ends of the rear side suction passages 63a to 63e are open to the swash plate chamber 31. In this way, the front side suction passages 61a to 61e communicate the second shaft hole 23 with the swash plate chamber 31. Similarly, the rear suction passages 63a to 63e communicate the third shaft hole 25 with the swash plate chamber 31.
- the first discharge passage 212 and the second discharge passage 221 are in communication with each other.
- the first cylinder bores 21a to 21e and the second cylinder bores 22a to 22e are coaxial with each other and face each other with the swash plate chamber 31 in between.
- the second shaft hole 23 and the third shaft hole 25 are coaxial with each other and face each other with the swash plate chamber 31 in between.
- the gasket 20 seals between the first cylinder block 21 and the second cylinder block 22 in a state where the first and second recesses 210 and 220 and the first and second discharge passages 212 and 221 are communicated with each other. It's stopped.
- the first valve forming plate 8 is provided between the front housing 17 and the first cylinder block 21.
- the front housing 17 and the first cylinder block 21 are joined in the axial center O direction via the first valve forming plate 8.
- the first valve forming plate 8 has a first valve plate 80, a first discharge valve plate 82, and a first retainer plate 83.
- the first valve plate 80 is formed with five first discharge holes 811 communicating with the first cylinder bores 21a to 21e.
- the first cylinder bores 21a to 21e communicate with the first discharge chamber 27 through the first discharge holes 811.
- the first discharge valve plate 82 is provided on the front surface of the first valve plate 80.
- the first discharge valve plate 82 is provided with five first discharge lead valves 82a capable of opening and closing each first discharge hole 811 by elastic deformation.
- the first retainer plate 83 is provided on the front surface of the first discharge valve plate 82. The first retainer plate 83 regulates the maximum opening degree of the first discharge lead valve 82a.
- the first valve forming plate 8 is formed with a first through hole 8a and a first communication hole 8b.
- the first through hole 8a and the first communication hole 8b penetrate the first valve plate 80, the first discharge valve plate 82, and the first retainer plate 83, respectively.
- the first shaft hole 173 and the second shaft hole 23 are communicated with each other by the first through hole 8a.
- the first discharge chamber 27 and the first discharge passage 212 are communicated with each other by the first communication hole 8b.
- the second valve forming plate 9 is provided between the second cylinder block 22 and the rear housing 19.
- the second cylinder block 22 and the rear housing 19 are joined in the axial center O direction via the second valve forming plate 9.
- the support projection 240 forms the second valve forming plate 9. It is in a state of protruding into the control pressure chamber 28 beyond.
- the second valve forming plate 9 has a second valve plate 90, a second discharge valve plate 92, and a second retainer plate 93.
- the second valve plate 90 is formed with five second discharge holes 911 communicating with the second cylinder bores 22a to 22e.
- the second cylinder bores 22a to 22e communicate with the second discharge chamber 29 through the second discharge holes 911.
- the second discharge valve plate 92 is provided on the rear surface of the second valve plate 90.
- the second discharge valve plate 92 is provided with five second discharge lead valves 92a capable of opening and closing each second discharge hole 911 by elastic deformation.
- the second retainer plate 93 is provided on the rear surface of the second discharge valve plate 92. The second retainer plate 93 regulates the maximum opening degree of the second discharge lead valve 92a.
- the second valve forming plate 9 is formed with a second through hole 9a and a second communication hole 9b.
- the second through hole 9a and the second communication hole 9b penetrate the second valve plate 90, the second discharge valve plate 92, and the second retainer plate 93, respectively.
- the support projection 240 of the second cylinder block 22 is inserted into the second through hole 9a.
- the second discharge chamber 29 and the second discharge passage 221 are communicated with each other by the second communication hole 9b.
- the first discharge chamber 27 and the second discharge chamber 29 communicate with each other through the first and second discharge passages 212 and 221 and the first and second communication holes 8b and 9b.
- the first discharge chamber 27 and the second discharge chamber 29 communicate with the discharge port 213 through the first and second discharge passages 212 and 221 and the first and second communication holes 8b and 9b.
- the drive shaft 3 extends from the front side to the rear side of the housing 1 in the axial direction O direction.
- the drive shaft 3 is made of steel and has rigidity against a compressive load of a high-pressure refrigerant gas.
- a screw hole 3a is formed in the drive shaft 3.
- the screw hole 3a opens at the front end of the drive shaft 3 and extends rearward in the drive shaft 3.
- the drive shaft 3 is connected to the power transmission mechanism 4 via the screw hole 3a. That is, the compressor of the embodiment has the power transmission mechanism 4.
- the power transmission mechanism 4 for example, a known pulley, an electromagnetic clutch, or the like can be adopted.
- the power transmission mechanism 4 is shown in a simplified manner for ease of explanation.
- the drive shaft 3 is formed with an axle path 33, a path 35, a connecting path 37, and a guide window 39.
- the axis 33 has a columnar shape.
- the axis 33 is open at the rear end of the drive shaft 3 and extends forward in the drive shaft 3 in the axial O direction.
- the axis 33 has a large-diameter portion 33a and a small-diameter portion 33b. Further, a step portion 33c is formed between the large diameter portion 33a and the small diameter portion 33b.
- the route 35 is located substantially in the center of the drive shaft 3 in the front-rear direction.
- the route 35 extends in the radial direction of the drive shaft 3 while being connected to the small diameter portion 33b of the shaft road 33, and is open to the outer peripheral surface 300 of the drive shaft 3.
- the path 35 may have a shape that penetrates the drive shaft 3 in the radial direction.
- the connecting path 37 is located on the drive shaft 3 in front of the path 35.
- the connecting path 37 extends in the radial direction of the drive shaft 3 while being connected to the small diameter portion 33b of the shaft path 33, and is open to the outer peripheral surface 300 of the drive shaft 3.
- the connecting path 37 is composed of a first connecting path 37a and a second connecting path 37b.
- the first connecting path 37a extends linearly in the radial direction of the drive shaft 3 while being connected to the small diameter portion 33b.
- the second connecting path 37b is connected to the first connecting path 37a and is opened in a long hole shape in the circumferential direction of the drive shaft 3.
- the shape of the connecting path 37 can be appropriately designed.
- the guide window 39 is recessed in the radial direction of the drive shaft 3 from the outer peripheral surface 300 of the drive shaft 3 toward the axis O side.
- the guide window 39 is located on the outer peripheral surface 300 on the rear side of the path 35.
- the guide window 39 extends around the drive shaft 3 in the circumferential direction over half a circumference.
- the guide window 39 extends in the axial O direction.
- the guide window 39 communicates with the large diameter portion 33a of the shaft path 33.
- a portion of the drive shaft 3 located on the opposite side of the guide window 39 with the axis O in between is the main body portion 3b. As shown in FIG.
- the main body portion 3b has a semicircular gutter shape extending in the axial direction O direction facing the guide window 39.
- the guide window 39 may be formed larger than half a circumference in the circumferential direction of the drive shaft 3, or may be formed smaller than half a circumference in the circumferential direction of the drive shaft 3.
- the guide window 39 is located on the opposite side of the connecting path 37 with the axis O in between. That is, in the drive shaft 3, the guide window 39 and the connecting path 37 are formed with a phase shift of about 180 °. Further, in the drive shaft 3, the path 35 is formed so as to be out of phase with the guide window 39 and the connecting path 37 by about 90 °. Note that FIG. 8 shows a state in which the drive shaft 3 is rotated around the axis O from the positions shown in FIGS. 1 and 2. Further, in FIGS. 1 and 2, the phase of the path 35 is changed and shown in order to facilitate the explanation.
- the drive shaft 3 is formed with the first regulation surface 301, the second regulation surface 302, and the guide surface 303.
- the first regulation surface 301 extends in a planar shape in the radial direction of the drive shaft 3 from the outer peripheral surface 300, and faces the guide window 39 backward.
- the second regulation surface 302 extends in a plane in the radial direction of the drive shaft 3 from the outer peripheral surface 300 while facing the first regulation surface 301, and faces the guide window 39 forward.
- the guide surface 303 is located between the first regulation surface 301 and the second regulation surface 302, and extends in a plane in the axial direction O direction.
- the guide surface 303 constitutes an end surface of the main body portion 3b.
- a first holding groove 3c is formed on the outer peripheral surface 300 on the rear side of the guide window 39. More specifically, the first holding groove 3c is arranged at a position closer to the control pressure chamber 28 than the second valve forming plate 9 when the drive shaft 3 is supported by the third shaft hole 25.
- the first holding groove 3c is an example of the "holding groove” in the present disclosure.
- the first holding groove 3c has an annular shape that goes around the outer peripheral surface 300.
- the first seal ring 41a is held in the first holding groove 3c.
- the first seal ring 41a is an example of the "first sealing member" in the present disclosure.
- the shape of the first holding groove 3c is exaggerated for the sake of simplicity.
- the material of the first seal ring 41a is a resin material such as PTFE (polytetrafluoroethylene) or PEEK (polyetheretherketone). As shown in FIGS. 11 to 13, the first seal ring 41a is formed in an annular shape. Further, the first seal ring 41a has a rectangular cross section in the radial direction. The first seal ring 41a has a rigidity that does not substantially elastically deform in the axial O direction or the radial direction.
- the drive shaft 3 is supported by the second shaft hole 23 and the third shaft hole 25 with the front end side including the screw hole 3a positioned in the first boss portion 171. As a result, it is rotatably inserted into the housing 1. As a result, the drive shaft 3 can rotate around the axis O. More specifically, in this embodiment, the drive shaft 3 rotates in the R1 direction shown in FIGS. 3 to 6.
- the first seal ring 41a comes into surface contact with the inner wall surface 251 of the third shaft hole 25 and the wall surface in the axial center O direction in the first holding groove 3c, respectively.
- the first seal ring 41a seals between the outer peripheral surface 300 of the drive shaft 3 and the inner wall surface 251 of the third shaft hole 25, thereby between the third shaft hole 25 and the control pressure chamber 28.
- the space between the swash plate chamber 31 and the control pressure chamber 28 is sealed.
- the length of the distance from the rear side passages 26a to 26e to the first seal ring 41a in the axial direction O direction is the third length L3.
- the first holding groove 3c on the outer peripheral surface 300 of the drive shaft 3 so that the distance in the axial center O direction from the rear side passages 26a to 26e to the first seal ring 41a is the third length L3.
- the position is designed.
- the third length L3 is longer than the second length L2, which is the minimum distance in the circumferential direction between the rear side passages 26a to 26e shown in FIG.
- the distance from the rear side passages 26a to 26e to the first seal ring 41a in the axial direction O direction is longer than the minimum distance in the circumferential direction between the rear side passages 26a to 26e.
- the third length L3 may be longer or shorter than the first length L1, which is the maximum distance between the rear side passages 26a to 26e in the circumferential direction. Further, the first length L1 and the third length L3 may be equal to each other.
- the first seal ring 41a rotates around the axis O together with the drive shaft 3 in the support projection 240, that is, in the third shaft hole 25 by rotating the drive shaft 3 around the axis O.
- the first seal ring 41a slides the inner wall surface 251 of the third shaft hole 25 around the axis O.
- the drive shaft 3 does not move in the axial center O direction while being supported by the second shaft hole 23 and the third shaft hole 25. Therefore, the first seal ring 41a does not move the inner wall surface 251 in the axial O direction.
- the first seal ring 41a is in a state of being pressed against the front wall surface of the first holding groove 3c by the action of the control pressure from the control pressure chamber 28 side. The control pressure will be described later.
- the guide window 39 is located in the third shaft hole 25 as shown in FIGS. 5 to 7.
- the guide window 39 faces the rear side passages 26a to 26e in the third shaft hole 25.
- the guide window 39 faces the rear side passages 26a to 26e communicating with the second compression chambers 45a to 45e in the re-expansion stroke or the suction stroke among the rear side passages 26a to 26e.
- the main body 3b faces the rear side passages 26a to 26e communicating with the second compression chambers 45a to 45e in the compression stroke or the discharge stroke.
- the guide window 39 and the main body portion 3b face the rear side suction passages 63a to 63e.
- the second compression chambers 45a to 45e will be described later.
- the connecting path 37 is located in the second shaft hole 23 as shown in FIG. As a result, in the second shaft hole 23, the connecting path 37 faces the front side connecting passages 24a to 24e. In this way, the connecting path 37 communicates the front side passages 24a to 24e with the axis 33. Further, in the second shaft hole 23, the connecting path 37 faces the front side suction passages 61a to 61e.
- the drive shaft 3 is supported by the housing 1, the front end side of the drive shaft 3 is inserted into the shaft sealing device 16 in the first shaft hole 173 as shown in FIGS. 1 and 2. As a result, the shaft sealing device 16 seals between the inside of the housing 1 and the outside of the housing 1.
- the fixed swash plate 5 is fixed to the drive shaft 3 by being press-fitted into the drive shaft 3.
- the fixed swash plate 5 is arranged in the swash plate chamber 31, and by rotating the drive shaft 3, it can rotate together with the drive shaft 3 in the swash plate chamber 31.
- the fixed swash plate 5 has a constant inclination angle with respect to a plane perpendicular to the drive shaft 3.
- a second boss portion 5a extending in the axial center O direction is formed on the fixed swash plate 5.
- a connecting path 5b is formed in the second boss portion 5a.
- the connecting path 5b extends in the radial direction of the drive shaft 3 and penetrates the second boss portion 5a.
- the connecting swash plate 5 is fixed to the drive shaft 3 so that the connecting swash plate 5b is aligned with the swash plate 35 and communicates with the swash plate 35.
- the path 35 connects the swash plate chamber 31 and the small diameter portion 33b of the shaft path 33 via the connecting path 5b. In this way, the shaft path 33 communicates with the swash plate chamber 31 via the connecting path 5b and the path 35.
- the first suction passage 30 is composed of the shaft path 33, the path 35, the connecting path 37, and the connecting path 5b.
- the suction passage 12 is composed of the first suction passage 30, the front side suction passages 61a to 61e, and the rear side suction passages 63a to 63e.
- a first thrust bearing 6a is provided between the first cylinder block 21 and the second boss portion 5a.
- a second thrust bearing 6b is provided between the second cylinder block 22 and the second boss portion 5a.
- Each piston 7 has a first head 7a, a second head 7b, and an engaging portion 7c.
- the first head 7a is an example of the "other side head” in the present disclosure
- the second head 7b is an example of the "one side head” in the present disclosure.
- the first head 7a is located on the front side of the piston 7, that is, on the first cylinder block 21 side.
- the first head 7a is housed in the first cylinder bores 21a to 21e, respectively.
- the first head 7a and the first valve forming plate 8 form the first compression chambers 43a to 43e in the first cylinder bores 21a to 21e, respectively, as shown in FIG.
- the first compression chambers 43a to 43e are examples of the "other side compression chamber" in the present disclosure.
- the first compression chambers 43a to 43e communicate with the front side passages 24a to 24e, respectively.
- the second head 7b is located on the rear side of the piston 7, that is, on the second cylinder block 22 side.
- the second head 7b is housed in the second cylinder bores 22a to 22e, respectively.
- the second head 7b and the second valve forming plate 9 form the second compression chambers 45a to 45e in the second cylinder bores 22a to 22e, respectively, as shown in FIGS. 4 to 7.
- the second compression chambers 45a to 45e are an example of the "one-sided compression chamber" in the present disclosure.
- the second compression chambers 45a to 45e communicate with the rear side passages 26a to 26e, respectively.
- the engaging portion 7c is located between the first head 7a and the second head 7b in the piston 7.
- Hemispherical shoes 14a and 14b are provided in the engaging portion 7c, respectively.
- the piston 7 is connected to the fixed swash plate 5 by these shoes 14a and 14b.
- the shoes 14a and 14b function as a conversion mechanism that converts the rotation of the fixed swash plate 5 into the reciprocating motion of the piston 7. Therefore, in the piston 7, the first head 7a can reciprocate in the first cylinder bores 21a to 21e between the top dead center and the bottom dead center of the first head 7a, and the second head 7a is reciprocated.
- the head 7b can reciprocate in the second cylinder bores 22a to 22e between the top dead center and the bottom dead center of the second head 7b.
- the second head 7b is at the bottom dead center of the second head 7b. Then, when the first head 7a is at the bottom dead center of the first head 7a, the second head 7b is at the top dead center of the second head 7b.
- the top dead center and bottom dead center of the first head 7a and the top dead center and bottom dead center of the second head 7b will be described as top dead center and bottom dead center, respectively.
- the moving body 11 is composed of a first moving body 11a and a second moving body 11b.
- the first moving body 11a is formed in a semicircular gutter shape consistent with the guide window 39, and extends in the axial direction O direction as shown in FIGS. 11 to 13. ing.
- the length in the axial center O direction of the first moving body 11a that is, the length in the front-rear direction is set shorter than the length in the front-rear direction of the guide window 39.
- the first moving body 11a has an outer surface 111, an inner surface 112, a front end surface 113, and a rear end surface 114.
- first moving body 11a is formed with an engaging portion 110 and a moving body passage 47.
- the moving body passage 47 is an example of the “second continuous passage” in the present disclosure.
- the engaging portion 110 is located at the rear end of the first moving body 11a and extends from the inner surface 112 in the radial direction of the first moving body 11a.
- the moving body passage 47 is located on the front side of the engaging portion 110 in the first moving body 11a, and penetrates the first moving body 11a in the radial direction. Further, as shown in FIG. 8, the moving body passage 47 is formed in the first moving body 11a so as to extend in the front-rear direction.
- the moving body passage 47 is gradually formed larger in the circumferential direction of the first moving body 11a from the front end to the rear end. That is, the first portion 47a formed large in the circumferential direction of the first moving body 11a is located on the rear end side of the moving body passage 47, and the second portion formed small in the circumferential direction of the first moving body 11a. 47b is located on the front end side of the moving body passage 47.
- the shape of the moving body passage 47 can be appropriately designed.
- the second moving body 11b has a main body portion 115 and a shaft portion 116. As shown in FIGS. 11 to 13, the main body 115 is formed in a substantially columnar shape having substantially the same diameter as the large diameter portion 33a of the shaft path 33. A second holding groove 115a is formed on the rear end side of the main body 115. The second holding groove 115a has an annular shape that goes around the main body 115. In FIG. 8 and the like, the shape of the second holding groove 115a is exaggerated for the sake of simplicity.
- a second seal ring 41b is provided in the second holding groove 115a.
- the second seal ring 41b is an example of the "second sealing member" in the present disclosure.
- the second seal ring 41b has the same configuration as the first seal ring 41a except that it is formed in an annular shape having a diameter smaller than that of the first seal ring 41a. That is, the material of the second seal ring 41b is also a resin material such as PTFE or PEEK. Further, the second seal ring 41b also has a rectangular cross section in the radial direction, and has rigidity to such an extent that it is not substantially elastically deformed in the axial center O direction or the radial direction.
- an engaging groove 117 is recessed on the front end side of the main body 115.
- the engaging groove 117 has an annular shape that goes around the main body 115 once.
- the shaft portion 116 is connected to the front end surface of the main body portion 115 and extends forward.
- the shaft portion 116 is formed in a columnar shape having a diameter smaller than that of the main body portion 115 and the small diameter portion 33b of the shaft path 33.
- the suction valve body 13 is integrally provided at the front end of the shaft portion 116, that is, the front end of the second moving body 11b. As shown in FIGS. 14 and 15, the suction valve body 13 is formed in a columnar shape having substantially the same diameter as the small diameter portion 33b of the shaft path 33.
- the second moving body 11b and the suction valve body 13 are inserted into the shaft path 33 from the rear end of the drive shaft 3.
- the main body 115 of the second moving body 11b is located in the large diameter portion 33a of the shaft path 33. Therefore, suction pressure acts on the front end surface of the main body 115 through the connecting path 5b, the path 35, and the axial path 33, that is, the first suction passage 30.
- the control pressure of the control pressure chamber 28 acts on the rear end surface of the main body 115.
- the second seal ring 41b is located between the second holding groove 115a and the inner peripheral surface 331 of the large diameter portion 33a.
- the second seal ring 41b comes into surface contact with the inner peripheral surface 331 of the large-diameter portion 33a and the wall surface in the axial center O direction of the second holding groove 115a, respectively.
- the second seal ring 41b seals between the main body portion 115 and the inner peripheral surface 331 so that the shaft path 30 and the control pressure chamber 28, and thus the swash plate chamber 31 and the control pressure chamber 28 The space is sealed.
- the second seal ring 41b is also in a state of being pressed against the wall surface on the front side of the second holding groove 115a by the action of the control pressure from the control pressure chamber 28 side.
- the suction valve body 13 is located on the front end side of the small diameter portion 33b of the shaft path 33.
- the first moving body 11a is provided in the guide window 39 with the inner surface 112 facing the second moving body 11b.
- the first moving body 11a is located on the opposite side of the main body 3b of the drive shaft 3 with the axis O in between, and is exposed in the third shaft hole 25.
- the first moving body 11a since the first moving body 11a has a semicircular girder shape having substantially the same diameter as the guide window 39, the first moving body 11a is inside the guide window 39 as shown in FIGS. 5 to 7.
- a cylindrical body having substantially the same diameter as the third shaft hole 25 is formed together with the main body portion 3b.
- the first moving body 11a is aligned with the third shaft hole 25 together with the main body portion 3b.
- the outer surface 111 faces the inner wall surface 251 of the third shaft hole 25.
- the engaging portion 110 enters the engaging groove 117 of the second moving body 11b.
- the engaging portion 110 and the engaging groove 117 are engaged with each other, so that the first moving body 11a and the second moving body 11b are assembled.
- the moving body passage 47 of the first moving body 11a communicates with the axial path 33 and, by extension, the first suction passage 30.
- the first moving body 11a and the second moving body 11b can be integrally moved in the axial center O direction. Specifically, as shown in FIG. 11, if the second moving body 11b moves backward in the axis 33, the first moving body 11a moves backward in the guide window 39. Then, as shown in FIG. 13, if the second moving body 11b moves forward in the axial path 33, the first moving body 11a moves forward in the guide window 39.
- an urging spring 51 is provided between the step portion 33c and the main body portion 115 of the second moving body 11b in the large diameter portion 33a.
- the urging spring 51 urges the second moving body 11b toward the rear of the drive shaft 3.
- the drive shaft 3 rotates around the axis O, so that the rotation of the drive shaft 3 is transmitted to the first moving body 11a through the guide surface 303.
- the first moving body 11a and thus the moving body 11, can rotate around the axis O together with the drive shaft 3.
- the second moving body 11b rotates around the axis O independently of the first moving body 11a in the large-diameter portion 33a. Is regulated.
- the second seal ring 41b and the second moving body 11b center the large diameter portion 33a of the axial path 33. Move in the O direction.
- the second seal ring 41b slides on the inner peripheral surface 331 of the large diameter portion 33a in the axial direction O direction.
- the second seal ring 41b since the second moving body 11b is restricted from rotating around the axis O independently of the first moving body 11a in the large-diameter portion 33a, the second seal ring 41b has an inner circumference.
- the surface 331 does not slide around the axis O.
- the moving body passage 47 intermittently communicates with the rear side communication passages 26a to 26e and the rear side suction passages 63a to 63e. Then, the communication area between the rear side passages 26a to 26e and the moving body passage 47 per one rotation of the drive shaft 3 changes according to the position of the first moving body 11a in the guide window 39, and the rear side suction is performed. The communication area between the passages 63a to 63e and the moving body passage 47 changes.
- FIGS. 5 to 7 in order to facilitate the explanation, the shape of the moving body passage 47 and the like is shown in a simplified manner, and the urging spring 51 is not shown.
- the connecting passage 37 becomes the front side connecting passages 24a to 24e and the front side suction passages 61a to 61e. Intermittent communication. Then, as shown in FIGS. 14 and 15, the communication area between the connecting path 37 and the axial path 33 increases according to the position of the suction valve body 13 in the axial path 33, more specifically, in the small diameter portion 33b. Change. As a result, in this compressor, the communication area between the front side communication passages 24a to 24e and the communication path 37 per rotation of the drive shaft 3 changes. Then, the connecting passage 37 communicates with the front side connecting passages 24a to 24e, so that the front side connecting passages 24a to 24e and the front side suction passages 61a to 61e communicate with each other via the connecting passage 37.
- the control valve 15 is provided in the rear housing 19. Further, a detection passage 15a is formed over the rear housing 19 and the second cylinder block 22. Further, the rear housing 19 is formed with a first air supply passage 15b and a second air supply passage 15c.
- the detection passage 15a is connected to the swash plate chamber 31 and the control valve 15.
- the first air supply passage 15b is connected to the second discharge chamber 29 and the control valve 15.
- the second air supply passage 15c is connected to the control pressure chamber 28 and the control valve 15. A part of the refrigerant gas in the second discharge chamber 29 is introduced into the control pressure chamber 28 through the first and second air supply passages 15b and 15c and the control valve 15.
- control pressure chamber 28 is connected to the swash plate chamber 31 by an air extraction passage (not shown).
- the refrigerant gas in the control pressure chamber 28 is led out to the swash plate chamber 31 by the bleed air passage.
- the control valve 15 adjusts the valve opening degree by sensing the suction pressure, which is the pressure of the refrigerant gas in the swash plate chamber 31, through the detection passage 15a.
- the control valve 15 adjusts the flow rate of the refrigerant gas introduced from the second discharge chamber 29 into the control pressure chamber 28 via the first and second air supply passages 15b and 15c.
- control valve 15 increases the valve opening degree to reduce the flow rate of the refrigerant gas introduced from the second discharge chamber 29 to the control pressure chamber 28 via the first and second air supply passages 15b and 15c. Increase.
- control valve 15 reduces the flow rate of the refrigerant gas introduced from the second discharge chamber 29 into the control pressure chamber 28 via the first and second air supply passages 15b and 15c by reducing the valve opening degree.
- the control valve 15 changes the flow rate of the refrigerant gas introduced from the second discharge chamber 29 into the control pressure chamber 28 with respect to the flow rate of the refrigerant gas led out from the control pressure chamber 28 to the swash plate chamber 31.
- Controls the control pressure which is the pressure of the refrigerant gas in the control pressure chamber 28.
- the drive shaft 3 rotates around the axis O, so that the fixed swash plate 5 rotates in the swash plate chamber 31.
- the first head 7a reciprocates in the first cylinder bores 21a to 21e between the top dead center and the bottom dead center, and the second head 7b top dead in the second cylinder bores 22a to 22e. It reciprocates between the point and bottom dead center.
- the re-expansion stroke in which the internal refrigerant gas re-expands, the suction stroke in which the refrigerant gas is sucked into the inside, and the internal refrigerant gas are compressed.
- the compression stroke to be performed and the discharge stroke to discharge the compressed refrigerant gas to the first discharge chamber 27 and the second discharge chamber 29 are repeatedly performed.
- the refrigerant gas in the first and second discharge chambers 27 and 29 is discharged to the condenser via the first and second communication holes 8b and 9b, the first and second discharge passages 212 and 221 and the discharge port 213.
- the first compression chamber 43a shown in FIG. 3 is in the initial stage of the re-expansion stroke to the suction stroke.
- the suction stroke is advanced as compared with the first compression chamber 43a, which is the middle stage of the suction stroke.
- the first head 7a of the piston 7 becomes the bottom dead center, and the suction stroke is shifted to the compression stroke. That is, in the first compression chamber 43c, the state is in a state of shifting from the late stage of the suction stroke to the early stage of the compression stroke.
- the compression stroke is advanced as compared with the first compression chamber 43c, which is the middle stage of the compression stroke. Then, in the first compression chamber 43e, the state shifts from the latter stage of the compression stroke to the discharge stroke.
- the first head 7a is not shown for the sake of simplicity.
- the second connecting path 37b has front side passages 24a to 24e communicating with the first compression chambers 43a to 43e in the initial stage of the re-expansion stroke to the suction stroke, and the middle stage of the suction stroke. It faces the front side communication passages 24a to 24e communicating with the first compression chambers 43a to 43e in the above. That is, when the rotation angle of the drive shaft 3 is in the state shown in FIG. 3, the first compression chamber 43a is in the initial stage of the re-expansion stroke to the suction stroke, and the first compression chamber 43b is in the middle stage of the suction stroke. Therefore, the second connecting path 37b faces the front side connecting passage 24a and the front side connecting passage 24b. At this time, the second connecting passage 37b faces the front side suction passage 61a and the front side suction passage 61e.
- the second connecting passage 37b faces the front side connecting passage 24e and the front side connecting passage 24a.
- the first compression chamber 43e communicating with the front side communication passage 24e is in the initial stage of the re-expansion stroke to the suction stroke
- the first compression chamber 43a communicating with the front side communication passage 24a is the suction stroke. It is in the mid-term stage.
- the second connecting passage 37b faces the front side suction passage 61e and the front side suction passage 61a.
- the second connecting passage 37b communicates with the first compression chambers 43a to 43e in the initial stage of the re-expansion stroke to the suction stroke, and the front side communication passages 24a to The 24e and the front side communication passages 24a to 24e communicating with the first compression chambers 43a to 43e in the middle stage of the suction stroke are sequentially opposed to each other. Further, the connecting passage 37 sequentially faces the front side suction passages 61a to 61e.
- the second compression chamber 45a shown in FIGS. 5 to 7 is in the middle stage of the compression stroke.
- the compression stroke is advanced as compared with the second compression chamber 45a, which is a later stage of the compression stroke.
- the second head 7b of the piston 7 becomes the top dead center, and the state shifts from the discharge stroke to the initial stage of the re-expansion stroke to the suction stroke.
- the suction stroke is advanced as compared with the second compression chamber 45c, which is the middle stage of the suction stroke.
- the suction stroke is further advanced than in the second compression chamber 45d, which is the latter stage of the suction stroke. That is, of the second compression chambers 45a to 45e, the second compression chambers 45a and 45b are in a high pressure state, and the second compression chamber 45c is in a state of shifting from high pressure to low pressure. Then, the second compression chambers 45d and 45e are in a low pressure state.
- the first moving body 11a since the first moving body 11a is provided in the guide window 39, the first moving body 11a is on the rear side communicating with the second compression chambers 45a to 45e in the re-expansion stroke or the suction stroke. It faces the communication passages 26a to 26e. That is, when the drive shaft 3 is at the rotation angle shown in FIGS. 5 to 7, the first moving body 11a communicates with the rear side communication passage 26c communicating with the second compression chamber 45c and the rear communicating with the second compression chamber 45d. It faces the side communication passage 26d and the rear side communication passage 26e communicating with the second compression chamber 45e. At this time, the first moving body 11a faces the rear side suction passage 63c and the rear side suction passage 63d.
- the main body 3b of the drive shaft 3 faces the rear side passages 26a to 26e communicating with the second compression chambers 45a to 45e in the compression stroke or the discharge stroke. Therefore, when the drive shaft 3 is at the rotation angle shown in FIGS. 5 to 7, the main body 3b is connected to the rear side passage 26a communicating with the second compression chamber 45a and the rear side communicating with the second compression chamber 45b. It faces the communication passage 26b.
- the second compression chamber 45c is in a state of shifting from the discharge stroke to the initial stage of the re-expansion stroke to the suction stroke.
- the main body 3b also faces the rear side passage 26c for most of the period during which the second compression chamber 45c is in the discharge stroke. Further, the main body portion 3b faces the rear side suction passage 63e, the rear side suction passage 63a, and the rear side suction passage 63b.
- the second compression chambers 45b to 45d become the re-expansion stroke or the suction stroke, and the second compression chambers 45e and 45a become the compression strokes. Or it becomes a discharge stroke.
- the first moving body 11a faces the rear side passages 26b to 26d.
- the first moving body 11a faces the rear side suction passage 63b and the rear side suction passage 63c.
- the main body portion 3b faces the rear side continuous passages 26e and 26a, and faces the rear side suction passage 63d, the rear side suction passage 63e, and the rear side suction passage 63a.
- the first moving body 11a sequentially faces the rear side passages 26a to 26e communicating with the second compression chambers 45a to 45e in the re-expansion stroke or the suction stroke, and the main body portion.
- the 3b sequentially faces the rear side communication passages 26a to 26e communicating with the second compression chambers 45a to 45e in the compression stroke or the discharge stroke.
- the first moving body 11a and the main body 3b sequentially face the rear suction passages 63a to 63e.
- the control valve 15 opens the valve.
- the control valve 15 reduces the control pressure in the control pressure chamber 28.
- the variable differential pressure which is the differential pressure between the control pressure and the suction pressure, becomes small.
- the second moving body 11b starts to move backward in the axial center O direction from the position shown in FIG. 13 by the urging force of the urging spring 51 in the large diameter portion 33a of the axial path 33. .. Therefore, the first moving body 11a starts to move backward in the guide window 39 in the axial direction O direction.
- the moving body passage 47 moves rearward with respect to the rear side continuous passages 26a to 26e and the rear side suction passages 63a to 63e. In this way, the moving body passage 47 communicates with the rear side passages 26a to 26e at a position close to the second portion 47b.
- the communication area between the rear side communication passages 26a to 26e and the moving body passage 47 per one rotation of the drive shaft 3 is gradually reduced.
- the outer surface 111 of the first moving body 11a begins to close the rear suction passages 63a to 63e. Therefore, the communication area between the rear suction passages 63a to 63e and the moving body passage 47 per rotation of the drive shaft 3 is gradually reduced.
- the suction valve body 13 starts to move backward in the small diameter portion 33b of the axial path 33 in the axial center O direction from the position shown in FIG. .. As a result, the suction valve body 13 begins to close the first connecting path 37a in the small diameter portion 33b, so that the communication area between the axial path 33 and the connecting path 37 gradually decreases.
- control valve 15 further reduces the valve opening degree and further reduces the control pressure in the control pressure chamber 28, so that the variable differential pressure is minimized.
- the second moving body 11b is in a state of being moved most rearward in the large diameter portion 33a.
- the first moving body 11a is in a state of being moved most rearward in the guide window 39, and the rear end surface 114 and the second regulation surface 302 come into contact with each other.
- the movement of the first moving body 11a to the rear is restricted.
- the rearward movement of the second moving body 11b through the first moving body 11a is also restricted.
- the first moving body 11a moves to the rearmost position in the guide window 39, so that the moving body passage 47 communicates with the rear side passages 26a to 26e at the second portion 47b.
- the communication area between the rear side communication passages 26a to 26e and the moving body passage 47 per one rotation of the drive shaft 3 is minimized.
- the outer surface 111 closes the rear side suction passages 63a to 63e. Therefore, the rear suction passages 63a to 63e and the moving body passage 47 are not communicated with each other.
- the first moving body 11a communicates the rear side communication passage 26c and the moving body passage 47.
- the second compression chamber 45c through which the rear side passage 26c communicates shifts from the discharge stroke to the initial stage of the re-expansion stroke to the suction stroke.
- the second compression chamber 45c is in the initial stage of the re-expansion stroke or the suction stroke.
- the rear side connecting passages 26d and 26e and the moving body passage 47 are not communicated by the outer surface 111, and the rear side suction passage 63c and the rear side suction passage 63d and the moving body passage are not communicated with each other.
- Make 47 and 47 non-communication That is, the first moving body 11a communicates with the moving body passage 47 only in the rear side communication passages 26a to 26e communicating with the second compression chambers 45a to 45e in the initial stage of the re-expansion stroke to the suction stroke.
- the main body 3b of the drive shaft 3 faces the rear side passages 26a to 26e communicating with the second compression chambers 45a to 45e in the compression stroke or the discharge stroke, so that the second body portion 3b is in the compression stroke or the discharge stroke.
- the rear side passages 26a to 26e communicating with the compression chambers 45a to 45e and the moving body passage 47 are not communicated with each other.
- the main body portion 3b moves to the rear side suction passage 63a, the rear side suction passage 63b, and the rear side suction passage 63e by closing the rear side suction passage 63a, the rear side suction passage 63b, and the rear side suction passage 63e.
- the body passage 47 is disconnected from the body passage 47.
- the second compression chambers 45a to 45e are filled with the connecting path 5b, the path 35, the axial path 33, the moving body passage 47 and the rear only when the suction stroke is in the initial stage.
- Refrigerant gas is sucked from the swash plate chamber 31 through the side passages 26a to 26e.
- the rear intake passages 63a to 63e are all closed by the outer surface 111 of the first moving body 11a and the main body 3b of the drive shaft 3, the refrigerant gas in the swash plate chamber 31 is the rear intake passages 63a to 63e.
- variable differential pressure is minimized, and the second moving body 11b moves most rearward in the large diameter portion 33a, so that the suction valve body 13 is in the small diameter portion 33b of the shaft path 33, as shown in FIG. Further moves backward in the O direction of the axis.
- the suction valve body 13 closes the first connecting path 37a in the small diameter portion 33b. Therefore, the axis 33 and the connecting path 37 are not communicated with each other.
- the second connecting path 37b when the variable differential pressure is the minimum, the second connecting path 37b, and thus the connecting path 37, has a first compression chamber in the initial stage of the suction stroke or the middle stage of the suction stroke due to the rotation of the drive shaft 3. Although it faces the front side communication passages 24a to 24e communicating with 43a to 43e, the communication area between the front side communication passages 24a to 24e and the connecting path 37 is substantially zero.
- the front side of the front side suction passages 61a to 61e facing the second connecting passage 37b such as the front side suction passage 61a and the front side suction passage 61e shown in FIG.
- the suction passages 61a to 61e communicate with the connecting path 37.
- the refrigerant gas in the swash plate chamber 31 passes through the front side suction passages 61a to 61e, the connecting passage 37, and the front side communication passages 24a to 24e in the first compression chamber 43a in the initial stage of the suction stroke or the middle stage of the suction stroke. Inhaled to ⁇ 43e.
- the refrigerant gas in the swash plate chamber 31 passes through the front side suction passages 61a and 61e, the connecting passages 37, and the front side communication passages 24a and 24b. It is sucked into the compression chambers 43a and 43b.
- the control valve 15 increases the valve opening degree. As a result, the flow rate of the refrigerant gas introduced from the second discharge chamber 29 into the control pressure chamber 28 is increased. In this way, the control valve 15 increases the control pressure in the control pressure chamber 28. As a result, the variable differential pressure becomes large.
- the second moving body 11b resists the urging force of the urging spring 51 in the large-diameter portion 33a of the axial path 33, and moves forward in the axial O direction from the position shown in FIG. Start moving. Therefore, the first moving body 11a starts to move forward in the guide window 39 in the axial direction O direction. As a result, the moving body passage 47 moves forward relative to the rear side continuous passages 26a to 26e and the rear side suction passages 63a to 63e. In this way, the moving body passage 47 communicates with the rear side passages 26a to 26e at a position close to the first portion 47a.
- the communication area between the rear side communication passages 26a to 26e and the moving body passage 47 per one rotation of the drive shaft 3 gradually increases. Further, at this time, as shown in FIG. 12, the outer surface 111 of the first moving body 11a begins to open the rear side suction passages 63a to 63e. Therefore, the communication area between the rear suction passages 63a to 63e and the moving body passage 47 per one rotation of the drive shaft 3 is gradually increased.
- the first moving body 11a communicates the rear side communication passages 26c and 26d with the moving body passage 47. Then, the first moving body 11a makes the rear side communication passage 26e and the moving body passage 47 non-communication by the outer surface 111. Further, the rear side suction passage 63c and the rear side suction passage 63d communicate with the moving body passage 47. That is, the first moving body 11a has a rear side passage 26a to 26e communicating with the second compression chambers 45a to 45e in the initial stage of the re-expansion stroke to the suction stroke, and a second compression chamber in the middle stage of the suction stroke.
- the moving body passage 47 and the rear suction passages 63a to 63e are communicated with the rear side passages 26a to 26e communicating with the 45a to 45e. Further, the main body 3b of the drive shaft 3 faces the rear side passages 26a to 26e communicating with the second compression chambers 45a to 45e in the compression stroke or the discharge stroke. At this time, the main body portion 3b continues to have no communication with the moving body passage 47 for the rear side suction passages 63a to 63e facing itself.
- the connecting path 5b, the path 35, the axial path 33, and the moving path 5b, the path 35, and the axial path 33 move into the second compression chambers 45a to 45e from the initial stage to the middle stage of the suction stroke.
- Refrigerant gas is sucked from the swash plate chamber 31 through the body passage 47 and the rear side passages 26a to 26e.
- the refrigerant gas is sucked into the second compression chambers 45a to 45e from the swash plate chamber 31 also through the rear side suction passages 63a to 63e, the moving body passage 47, and the rear side continuous passages 26a to 26e.
- variable differential pressure becomes large, and the moving body 11 starts to move forward in the axial center O direction, so that the suction valve body 13 moves in the small diameter portion 33b of the axial path 33 from the position shown in FIG. Start moving forward in the direction.
- the suction valve body 13 starts to open the first connecting path 37a in the small diameter portion 33b, so that the communication area between the axial path 33 and the connecting path 37 gradually increases.
- the communication area between the front side communication passages 24a to 24e and the communication path 37 per one rotation of the drive shaft 3 becomes larger than zero. Therefore, for the first compression chambers 43a to 43e in the initial stage of the suction stroke and the middle stage of the suction stroke, through the connecting path 5b, the path 35, the axial path 33, the connecting path 37, and the front side communication passages 24a to 24e. Refrigerant gas is sucked from the swash plate chamber 31. Also at this time, the front side suction passages 61a to 61e facing the second connecting passage 37b are in the initial stage of the suction stroke and the middle stage of the suction stroke through the connecting passage 37 and the front side connecting passages 24a to 24e.
- Refrigerant gas is sucked into the first compression chambers 43a to 43e from the swash plate chamber 31. In this way, in this compressor, the flow rate of the refrigerant gas discharged from the first compression chambers 43a to 43e to the first discharge chamber 27 increases.
- the control valve 15 further increases the valve opening degree and further increases the control pressure of the control pressure chamber 28, so that the variable differential pressure becomes maximum.
- the second moving body 11b is in a state where it has moved most forward in the large diameter portion 33a.
- the first moving body 11a is in a state of being moved most forward in the guide window 39, and the front end surface 113 comes into contact with the first regulation surface 301.
- the forward movement of the first moving body 11a is restricted.
- the forward movement of the second moving body 11b through the first moving body 11a is also restricted.
- the second seal ring 41b moves to a position closer to the guide window 39 than the first seal ring 41a in the axial O direction. To do. Even in this case, the second seal ring 41b is not exposed from the guide window 39, and the shaft path 30 and the control pressure chamber 28 are continuously sealed.
- the moving body passage 47 communicates with the rear side passages 26a to 26e at the first portion 47a. In this way, in this compressor, the communication area between the rear side communication passages 26a to 26e and the moving body passage 47 per one rotation of the drive shaft 3 is maximized. Further, in this case, since the outer surface 111 of the first moving body 11a maximizes the opening degree of the rear side connecting passages 26a to 26e, the rear side suction passages 63a to 63e and the moving body per one rotation of the drive shaft 3 The communication area with the passage 47 is also maximized.
- the first moving body 11a communicates the rear side communication passages 26c to 26e with the moving body passage 47. Further, the rear side suction passage 63c and the rear side suction passage 63d communicate with the moving body passage 47. That is, the first moving body 11a has a rear side passage 26a to 26e communicating with the second compression chambers 45a to 45e in the initial stage of the re-expansion stroke to the suction stroke, and a second compression chamber in the middle stage of the suction stroke.
- the suction passages 63a to 63e are communicated with each other.
- the main body 3b of the drive shaft 3 faces the rear side passages 26a to 26e communicating with the second compression chambers 45a to 45e in the compression stroke or the discharge stroke. At this time, the main body portion 3b continues to have no communication with the moving body passage 47 for the rear side suction passages 63a to 63e facing itself.
- the inside of the swash plate chamber 31 is passed through the connecting path 5b, the path 35, the axis 33, the moving body passage 47, and the rear side connecting passages 26c, 26d, 26e.
- the refrigerant gas is sucked into the second compression chambers 45c, 45d, 45e, and the second from the inside of the swash plate chamber 31 through the rear side suction passages 63c, 63d, the moving body passage 47, and the rear side communication passages 26c, 26d, 26e.
- the refrigerant gas is sucked into the compression chambers 45c, 45d, 45e.
- the second compression chambers 45a to 45e have the connecting path 5b, the path 35, the axial path 33, and the moving body passage from the initial stage to the late stage of the suction stroke. Refrigerant gas is sucked from the swash plate chamber 31 through 47 and the rear side passages 26a to 26e.
- the outer surface 111 of the first moving body 11a maximizes the opening degree of the rear side suction passages 61a to 61e, the rear side suction passages 61a to 61e, the moving body passage 47, and the rear side continuous passages 26a to 26e are used.
- the flow rate of the refrigerant gas sucked from the swash plate chamber 31 into the second compression chambers 45a to 45e is maximized. That is, when the drive shaft 3 is at the rotation angle shown in FIG. 7, the second compression chamber 45c from the inside of the swash plate chamber 31 is passed through the rear side suction passages 63c and 63d, the moving body passage 47 and the rear side continuous passages 26c, 26d and 26e. , 45d, 45e maximizes the flow rate of the refrigerant gas sucked into.
- the flow rate of the refrigerant gas sucked from the swash plate chamber 31 into the second compression chambers 45a to 45e is maximized.
- the flow rate of the refrigerant gas discharged from the second compression chambers 45a to 45e to the second discharge chamber 29 is maximized.
- variable differential pressure is maximized, and the moving body 11 moves most forward in the axial center O direction, so that the suction valve body 13 is axially centered in the small diameter portion 33b of the axial path 33, as shown in FIG. Move most forward in the O direction.
- the suction valve body 13 maximizes the opening degree of the first connecting path 37a in the small diameter portion 33b, so that the communication area between the axial path 33 and the connecting path 37 is maximized.
- the communication area between the front side communication passages 24a to 24e and the communication path 37 per one rotation of the drive shaft 3 is maximized. Therefore, with respect to the first compression chambers 43a to 43e in the initial stage of the suction stroke and the middle stage of the suction stroke, through the connecting path 5b, the path 35, the axis path 33, the connecting path 37, and the front side communication passages 24a to 24e. The flow rate of the refrigerant gas sucked from the swash plate chamber 31 is maximized. Also at this time, the front side suction passages 61a to 61e facing the second connecting passage 37b are in the initial stage of the suction stroke and the middle stage of the suction stroke through the connecting passage 37 and the front side connecting passages 24a to 24e.
- Refrigerant gas is sucked into the first compression chambers 43a to 43e from the swash plate chamber 31.
- the flow rate of the refrigerant gas sucked from the swash plate chamber 31 into the first compression chambers 43a to 43e is maximized, so that the refrigerant gas is discharged from the first compression chambers 43a to 43e into the first discharge chamber 27.
- the flow rate of the refrigerant gas is maximized.
- the space between the swash plate chamber 31 and the control pressure chamber 28 is sealed by the first seal ring 41a provided on the drive shaft 3.
- the second seal ring 41b provided on the main body 115 of the second moving body 11b also seals between the swash plate chamber 31 and the control pressure chamber 28.
- the first seal ring 41a slides the inner wall surface 251 of the third shaft hole 25 around the axis by the drive shaft 3 rotating around the axis O
- the inner wall surface 251 of the third shaft hole 25 is slid. It does not slide in the O direction of the axis.
- the second seal ring 41b slides the inner peripheral surface 331 of the large-diameter portion 33a in the axial O direction by the second moving body 11b that moves in the axial O direction, the inner peripheral surface 331 is the axial center O. It does not slide around. As a result, the first and second seal rings 41a and 41b are less likely to be worn in this compressor, and the first and second seal rings 41a and 41b provide a refrigerant between the swash plate chamber 31 and the control pressure chamber 28. It is possible to suitably prevent gas leakage.
- the first seal ring 41a is located in the support projection 240 by being housed in the first holding groove 3c formed on the outer peripheral surface 300 of the drive shaft 3.
- the first seal ring 41a is arranged at a position close to the control pressure chamber 28 in the axial center O direction, the control pressure of the control pressure chamber 28 is likely to act. Therefore, the first seal ring 41a is easily pressed against the first holding groove 3c in the axial O direction by the control pressure.
- the second seal ring 41b is easily pressed against the second holding groove 115 in the axial direction O direction.
- the first and second seal rings 41a and 41b can suitably seal between the swash plate chamber 31 and the control pressure chamber 28.
- the first holding groove 3c is controlled more than the second valve forming plate 9 on the outer peripheral surface 300 of the drive shaft 3 when the drive shaft 3 is supported in the third shaft hole 25. It is arranged at a location on the compression chamber 28 side.
- the first seal ring 41a housed in the first holding groove 3c and the first holding groove 3c is located at a position separated from the first compression chambers 45a to 45e and, by extension, the rear side passages 26a to 26e in the axial direction O direction. Is placed in. More specifically, in this compressor, the length of the distance from the rear side passages 26a to 26e to the first seal ring 41a in the axial direction O direction is the third length L3, and the rear side connection It is longer than the minimum distance in the circumferential direction between the passages 26a to 26e. As a result, the first seal ring 41a and the first holding groove 3c are arranged sufficiently apart from the rear side communication passages 26a to 26e in the axial O direction.
- the high-pressure refrigerant gas is the first. It becomes difficult to distribute to the first compression chambers 45a to 45e in the suction stroke or to the control pressure chamber 28 via the 1 holding groove 3c or the first holding groove 3c and the first seal ring 41a. There is.
- control pressure of the control pressure chamber 28 can be suitably adjusted by the control valve 15, and the moving body 11 is suitably moved in the axial O direction with respect to the drive shaft 3 based on the control pressure. It is possible.
- the compressor of Example 1 has excellent durability and exhibits high controllability.
- connection path 5b, the path 35, and the axial path 33 that is, the first suction passage 30, the moving body passage 47, and the rear side continuous passage 26a are connected to the second compression chambers 45a to 45e in the suction stroke.
- the refrigerant gas in the swash plate chamber 31 is sucked through the ⁇ 26e.
- the variable differential pressure becomes large, and the rear side suction passages 63a to 63e communicate with the moving body passage 47, so that the rear side suction passages 63a to 63e also refer to the second compression chambers 45a to 45e in the suction stroke.
- the refrigerant gas in the swash plate chamber 31 is sucked in.
- the refrigerant gas in the swash plate chamber 31 is sucked into the first compression chambers 43a to 43e in the suction stroke through the front side suction passages 61a to 61e and the front side communication passages 24a to 24e. Further, the variable differential pressure becomes large, and the axial path 33 and the connecting path 37 communicate with each other, so that the refrigerant gas in the swash plate chamber 31 becomes the first through the first suction passage 30 and the front side connecting passages 24a to 24e. It is sucked into the compression chambers 43a to 43e.
- the flow rate of the refrigerant gas sucked from the swash plate chamber 31 into the first and second compression chambers 43a to 43e and 45a to 45e can be sufficiently secured, so that the first and second compression chambers 43a can be sufficiently secured. From ⁇ 43e and 45a to 45e, it is possible to suitably increase the flow rate of the refrigerant gas discharged into the first and second discharge chambers 27 and 29.
- the swash plate chamber 31 is changed to the first and second compression chambers 43a to 43e and 45a to 45e by the first suction passage 30, the front side suction passages 61a to 61e and the rear side suction passages 63a to 63e.
- a sufficient flow rate of the sucked refrigerant gas can be secured. Therefore, the first suction passage 30, the front side suction passages 61a to 61e, and the rear side suction passages 63a to 63e are not excessively enlarged, and the swash plate chambers 31 to the first and second compression chambers 43a to 43e and 45a to 45e are used.
- the flow rate of the refrigerant gas sucked into the air can be suitably secured. Therefore, in this compressor, it is possible to suppress the increase in size of the drive shaft 3, and it is also possible to suppress the increase in size of the first and second cylinder blocks 21 and 22.
- the compressor of Example 1 can suppress the increase in size while exhibiting high performance.
- the swash plate chamber 31 is used as the suction region in the present disclosure, it is not necessary to separately provide a suction chamber or the like corresponding to the suction region in the housing 1. Therefore, the housing 1 can be easily formed. Further, the formation of the first suction passage 30 is facilitated by forming the first suction passage 30 by the connecting path 5b, the path 35, the axis path 33, and the connecting path 37.
- the suction valve body 13 is the drive shaft.
- the flow rate of the refrigerant gas sucked into the first compression chambers 43a to 43e is reduced per one rotation of 3.
- the moving body 11 increases the flow rate of the refrigerant gas sucked into the second compression chambers 45a to 45e per rotation of the drive shaft 3, so that the suction valve body 13 becomes the third drive shaft 3 per rotation. 1
- the flow rate of the refrigerant gas sucked into the compression chambers 43a to 43e is increased.
- the flow rate of the refrigerant gas discharged from the first and second compression chambers 43a to 43e and 45a to 45e to the first and second discharge chambers 27 and 29 per rotation of the drive shaft 3 is preferable. It is possible to adjust to.
- the main body 3b of the drive shaft 3 faces the rear side passages 26a to 26e communicating with the second compression chambers 45a to 45e in the compression stroke or the discharge stroke in the third shaft hole 25. To do.
- the main body portion 3b, and thus the drive shaft 3 makes the rear side communication passages 26a to 26e communicating with the second compression chambers 45a to 45e in the compression stroke or the discharge stroke non-communication with the moving body passage 47. Since the drive shaft 3 is made of steel, the drive shaft 3 can suitably receive the compression load from the second compression chambers 45a to 45e in the compression stroke and the discharge stroke.
- the compressive load is less likely to act on the first moving body 11a, and by extension, the moving body 11, so that the moving body 11 can easily move in the axial center O direction.
- a part of the high-pressure refrigerant gas compressed in the compression stroke goes into the second shaft hole 23 through the front side communication passages 24a to 24e communicating with the first compression chambers 43a to 43e in the compression stroke or the discharge stroke. And distribute.
- the drive shaft 3 is capable of receiving the compressive load from the first compression chambers 43a to 43e in the compression stroke and the discharge stroke. Therefore, it is difficult for the compression load to act on the suction valve body 13. In this respect as well, the compressor has high controllability.
- the inlet control is performed to change the flow rate of the refrigerant gas introduced from the second discharge chamber 29 to the control pressure chamber 28 through the first and second air supply passages 15b and 15c by the control valve 15.
- the control pressure chamber 28 can be quickly increased in pressure, and the flow rate of the refrigerant gas discharged from the first and second compression chambers 43a to 43e and 45a to 45e to the first and second discharge chambers 27 and 29 can be rapidly increased. Can be increased to.
- the extending portion can be easily provided on the second cylinder block 22.
- the fitting groove 241 is formed in the second cylinder block 22. Further, in this compressor, a fitting member 242 is provided on the second cylinder block 22.
- the fitting groove 241 is recessed from the rear end of the second cylinder block 22 toward the front in the axial O direction. Further, the second cylinder block 22 is provided with a fitting member 242. The fitting member 242 is fixed to the fitting groove 241 and eventually to the second cylinder block 22 by being press-fitted into the fitting groove 241. The fitting member 242 is formed in a tubular shape. As a result, in this compressor, the "extending portion" in the present disclosure is formed by the fitting member 242.
- the fitting member 242 may be formed of the same material as the second cylinder block 22, or may be formed of a material different from that of the second cylinder block 22.
- rear side communication passages 26a to 26e are formed so as to penetrate the second cylinder block 22 and the fitting member 242.
- the fitting member 242 is fixed to the second cylinder block 22 and is directed toward the control pressure chamber 28 side in the axial center O direction from the second cylinder bores 22a to 22e and the rear side passages 26a to 26e. It is extending. As a result, the fitting member 242 protrudes into the control pressure chamber 28.
- the third shaft hole 25 extends to the inside of the fitting member 242, and the inner wall surface 251 extends to the inside of the fitting member 242.
- this compressor the drive shaft 3 is supported by the third shaft hole 25, so that the first seal ring 41a is held in the first holding groove 3c, and the first holding groove 3c and the first holding groove 3c are held. It is located between the fitting member 242 and the portion on the control pressure chamber 28 side of the second valve forming plate 9.
- Other configurations in this compressor are the same as those in the compressor of the first embodiment, and the same configurations are designated by the same reference numerals and detailed description of the configurations will be omitted.
- This compressor can also perform the same operation as the compressor of the first embodiment. Further, in this compressor, by providing the fitting member 242 of another member with respect to the second cylinder block 22, it is possible to increase the degree of freedom in designing the extending portion. As a result, for example, it is easy to secure the strength of the fitting member 242 as the extending portion and to secure the slidability between the drive shaft 3 and the first seal ring 41a and the fitting member 242. ..
- the compressor of the present disclosure has been described in accordance with Examples 1 and 2, but the compressor of the present disclosure is not limited to the above Examples 1 and 2, and is appropriately used as long as the purpose is not deviated. Needless to say, it can be changed and applied.
- the swash plate chamber 31 is used as the suction region in the present disclosure.
- the suction chamber or the like may be used as a suction region by forming a suction chamber or the like that serves as a suction pressure in the housing 1. Then, even if the second shaft hole 23 and the suction chamber or the like are communicated with each other by the front side suction passages 61a to 61e, and the third shaft hole 25 and the suction chamber or the like are communicated with each other by the rear side suction passages 63a to 63e. good.
- the moving body 11 passes through the first suction passage 30, the moving body passage 47, and the rear side continuous passages 26a to 26e per one rotation of the drive shaft 3 from the inside of the swash plate chamber 31. 2
- the swash plate chamber 31 is passed through the rear side suction passages 63a to 63e, the moving body passage 47, and the rear side communication passages 26a to 26e.
- the flow rate of the refrigerant gas sucked into the second compression chambers 45a to 45e from the inside is set to zero.
- the present invention is not limited to this, when the flow rate of the refrigerant gas sucked into the second compression chambers 45a to 45e through the first suction passage 30, the moving body passage 47, and the rear side communication passages 26a to 26e is the minimum. Also, a certain amount of refrigerant gas is sucked from the inside of the swash plate chamber 31 into the second compression chamber 45a to 45e through the rear side suction passages 63a to 63e, the moving body passage 47, and the rear side communication passages 26a to 26e. You may.
- the moving body 11 changes the flow rate of the refrigerant gas discharged from the first compression chambers 43a to 43e to the first discharge chamber 27 per rotation of the drive shaft 3
- the suction valve body 13 changes the flow rate of the drive shaft 3.
- the flow rate of the refrigerant gas discharged from the second compression chambers 45a to 45e to the second discharge chamber 29 may be changed per one rotation of the above.
- the connecting passage 37 is formed in the drive shaft 3 so that the refrigerant gas is sucked into the first compression chambers 43a to 43e in the initial stage of the suction stroke to the latter stage of the suction stroke through the front side communication passages 24a to 24e. You may. Further, the connecting path 37 may be formed on the drive shaft 3 so that the refrigerant gas is sucked only into the first compression chambers 43a to 43e in the initial stage of the suction stroke through the front side communication passages 24a to 24e.
- the first compression chambers 43a to 43e perform suction work. It may be configured to be in a cylinder deactivation state in which compression work is not performed.
- the compressors of Examples 1 and 2 may be configured as single-headed piston type compressors in which the formation of the first compression chambers 43a to 43e is omitted.
- the rear per rotation of the drive shaft 3 depends on the position of the first moving body 11a in the guide window 39, that is, the position of the moving body 11 in the axial center O direction.
- the communication area between the side communication passages 26a to 26e and the moving body passage 47 By changing the communication area between the side communication passages 26a to 26e and the moving body passage 47, the flow rate of the refrigerant gas discharged from the second compression chambers 45a to 45e to the second discharge chamber 29 is changed.
- the flow rate of the refrigerant gas discharged from the second compression chambers 45a to 45e to the second discharge chamber 29 may be changed.
- external control may be performed to control the control pressure by switching ON and OFF of the current from the outside to the control valve 15, and the control may be performed regardless of the current from the outside.
- Internal control to control the pressure may be performed.
- the control valve 15 is configured to reduce the valve opening degree by turning off the current to the control valve 15, the valve opening degree is increased when the compressor is stopped. Can be reduced, and the control pressure in the control pressure chamber 28 can be lowered.
- the compressor can be started in the state where the flow rate of the refrigerant gas discharged from the first and second compression chambers 43a to 43e and 45a to 45e to the first and second discharge chambers 27 and 29 is the minimum, so that the start-up shock is reduced. can do.
- the extraction side control may be performed in which the flow rate of the refrigerant gas led out from the control pressure chamber 28 to the swash plate chamber 31 via the bleed air passage is changed by the control valve 15.
- the refrigerant in the second discharge chamber 29 used to change the flow rate of the refrigerant gas discharged from the first and second compression chambers 43a to 43e and 45a to 45e to the first and second discharge chambers 27 and 29. Since the amount of gas can be reduced, the efficiency of the compressor can be increased. Further, in this case, if the valve opening degree is increased by turning off the current to the control valve 15, the valve opening degree becomes large when the compressor is stopped, and the control pressure of the control pressure chamber 28 is increased. Can be lowered.
- the compressor can be started in the state where the flow rate of the refrigerant gas discharged from the first and second compression chambers 43a to 43e and 45a to 45e to the first and second discharge chambers 27 and 29 is the minimum, so that the start-up shock is reduced. can do.
- the first seal ring 41a is compressed and deformed in the radial direction between the inner wall surface 251 of the third shaft hole 25 and the first holding groove 3c, so that the swash plate chamber is formed.
- the space between 31 and the control pressure chamber 28 may be sealed.
- compressors of Examples 1 and 2 include the following inventions.
- a housing having a cylinder block in which a plurality of cylinder bores are formed, and a shaft hole, a discharge chamber, and a suction region having a lower pressure than the discharge chamber.
- a drive shaft rotatably supported in the shaft hole and A fixed swash plate that can be rotated in the housing by rotation of the drive shaft and has a constant inclination angle with respect to a plane perpendicular to the drive shaft.
- a piston that forms a compression chamber in each cylinder bore and is connected to the fixed swash plate, A suction passage for sucking the refrigerant in the suction region into the compression chamber, A discharge valve that discharges the refrigerant in the compression chamber to the discharge chamber, A moving body provided on the drive shaft, located in the shaft hole, rotating integrally with the drive shaft, and movable with respect to the drive shaft in the axial direction of the drive shaft based on a control pressure. , A control valve for controlling the control pressure is provided.
- the cylinder block is formed with a first passage that communicates with the cylinder bore.
- the moving body is formed with a second passage that intermittently communicates with the first passage as the drive shaft rotates.
- a piston-type compressor in which the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber changes according to the position of the moving body in the axial direction.
- the shaft hole has an inner wall surface through which the first continuous passage opens.
- the suction passage has a first suction passage formed on the drive shaft and a second suction passage formed on the cylinder block. The first suction passage communicates with the suction region and the second continuous passage.
- the second suction passage is a piston type compressor, wherein one end side is open to the suction region and the other end side is open to the inner wall surface so as to be able to communicate with the second continuous passage.
- the suction region is a swash plate chamber that rotatably accommodates the swash plate.
- the first suction passage extends in the drive shaft in the axial direction and communicates with the second communication passage, and extends in the radial direction of the drive shaft to communicate the swash plate chamber and the shaft. It has a route to be used.
- the cylinder bore is composed of a one-sided cylinder bore arranged on one side in the axial direction and a other-side cylinder bore arranged on the other side in the axial direction.
- the shaft hole has a one-sided shaft hole arranged on one side in the axial center direction and the other side shaft hole arranged on the other side in the axial center direction.
- the piston has a one-sided head that forms a one-sided compression chamber in the one-sided cylinder bore and a other-sided head that forms the other-side compression chamber in the other-sided cylinder bore.
- the first communication passage includes a one-sided first passage that communicates with the one-side cylinder bore and a other-side first passage that communicates with the other cylinder bore.
- the one-sided shaft hole has a one-sided inner wall surface through which the one-sided first continuous passage opens.
- the other side shaft hole has an inner wall surface on the other side through which the first continuous passage on the other side opens.
- the second passage communicates with the first passage on one side,
- the first suction passage has a connecting path extending in the radial direction of the drive shaft and communicating the shaft path with the first connecting passage on the other side.
- the second suction passage has a second suction passage on one side, one end of which opens into the swash plate chamber, and the other end of which opens on the inner wall surface of one side so as to communicate with the second passage.
- One end side is an opening on the inner wall surface on the other side so as to be able to communicate with the connecting path, and the other end side is a second suction passage on the other side opening in the swash plate chamber.
- the moving body has a first moving body in which the second continuous passage is formed and a second moving body connected to the first moving body and located in the axial path.
- the drive shaft is formed with a guide window that communicates with the shaft path and opens in the one-side shaft hole to arrange the first moving body.
- the first moving body communicates the first passage on one side with the second passage.
- the drive shaft makes the one-sided first passage and the second passage non-communication.
- the second moving body is located in the axial path, and if the flow rate of the refrigerant discharged from the one-side compression chamber to the discharge chamber decreases, the first suction passage allows the swash plate chamber to the other.
- a suction valve body that reduces the flow rate of the refrigerant to be sucked into the side compression chamber is connected.
- the compressor of the present disclosure can be used for a vehicle air conditioner or the like.
- Second shaft hole (shaft hole, other side shaft hole) 24a to 24e ... Front side passage (first side passage on the other side) 25 ...
- Second compression chamber (one-side compression chamber) 47 Moving body passage (second passage) 61a to 61e ... Front side suction passage (second suction passage, other side second suction passage) 63a-63e ... Rear side suction passage (second suction passage, one side second suction passage) 173 ... First shaft hole (shaft hole) 231 ... Inner wall surface (inner wall surface on the other side) 240 ... Support protrusion (extending part) 242 ... Fitting member (extending part) 251 ... Inner wall surface (inner wall surface on one side) O ... Axis
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Abstract
Description
前記軸孔内に回転可能に支承された駆動軸と、
前記駆動軸の回転によって前記ハウジング内で回転可能であり、前記駆動軸に垂直な平面に対する傾斜角度が一定である固定斜板と、
前記各シリンダボア内に圧縮室を形成し、前記固定斜板に連結されるピストンと、
前記吸入領域内の冷媒を前記圧縮室内に吸入させる吸入通路と、
前記圧縮室内の冷媒を前記吐出室に吐出させる吐出弁と、
前記駆動軸に設けられて前記軸孔内に位置し、前記駆動軸と一体回転するとともに、制御圧力に基づいて前記駆動軸の軸心方向に前記駆動軸に対して移動可能である移動体と、
前記制御圧力を制御する制御弁とを備え、
前記シリンダブロックには、前記シリンダボアに連通する第1連通路が形成され、
前記移動体には、前記駆動軸の回転に伴い間欠的に前記第1連通路と連通する第2連通路が形成され、
前記移動体の前記軸心方向の位置に応じて、前記圧縮室から前記吐出室に吐出される冷媒の流量が変化するピストン式圧縮機であって、
前記軸孔は、前記第1連通路が開口する内壁面を有し、
前記ハウジングは、前記駆動軸の軸心方向の一方側に配置され、前記吐出室及び前記制御圧室が形成されるとともに、前記吐出弁を介して前記シリンダブロックと前記軸心方向に接合される第1ハウジングを有し、
前記シリンダブロックは、前記軸心方向で前記制御圧室内に延びるとともに前記軸孔の一部が形成された延在部を有し、
前記吸入通路は、前記駆動軸に形成された第1吸入通路を有し、
前記第1吸入通路は、前記駆動軸内で前記軸心方向に延び、前記第2連通路に連通するとともに前記制御圧室に連通する軸路と、前記駆動軸の径方向に延び、前記斜板室と前記軸路とを連通する径路とを有し、
前記移動体は、前記第2連通路が形成された第1移動体と、第1移動体と連結されて前記軸路内に位置し、前記制御圧室と対向しつつ、前記軸路内を前記軸心方向に移動可能な第2移動体とを有し、
前記駆動軸には、環状に形成されて前記延在部内に位置し、前記軸心周りに回転する駆動軸によって前記内壁面を前記軸心周りに摺動しつつ、前記吸入領域と前記制御圧室との間を封止する第1封止部材が設けられ、
前記駆動軸の前記外周面には、環状に形成されて前記延在部内に位置し、前記第1封止部材を収容して保持する保持溝が形成され、
前記保持溝は、前記軸心方向において前記吐出弁よりも前記制御圧室側に配置されていることを特徴とする。
図1及び図2に示すように、実施例1の圧縮機は、ハウジング1と、駆動軸3と、固定斜板5と、複数のピストン7と、第1弁形成プレート8と、第2弁形成プレート9と、移動体11と、吸入通路12と、制御弁15とを備えている。第1、2弁形成プレート8、9は、本開示における「吐出弁」の一例である。
図16に示すように、実施例2の圧縮機では、第2シリンダブロック22に嵌合溝241が形成されている。また、この圧縮機では、第2シリンダブロック22に嵌合部材242が設けられている。
前記軸孔内に回転可能に支承された駆動軸と、
前記駆動軸の回転によって前記ハウジング内で回転可能であり、前記駆動軸に垂直な平面に対する傾斜角度が一定である固定斜板と、
前記各シリンダボア内に圧縮室を形成し、前記固定斜板に連結されるピストンと、
前記吸入領域内の冷媒を前記圧縮室内に吸入させる吸入通路と、
前記圧縮室内の冷媒を前記吐出室に吐出させる吐出弁と、
前記駆動軸に設けられて前記軸孔内に位置し、前記駆動軸と一体回転するとともに、制御圧力に基づいて前記駆動軸の軸心方向に前記駆動軸に対して移動可能である移動体と、
前記制御圧力を制御する制御弁とを備え、
前記シリンダブロックには、前記シリンダボアに連通する第1連通路が形成され、
前記移動体には、前記駆動軸の回転に伴い間欠的に前記第1連通路と連通する第2連通路が形成され、
前記移動体の前記軸心方向の位置に応じて、前記圧縮室から前記吐出室に吐出される冷媒の流量が変化するピストン式圧縮機であって、
前記軸孔は、前記第1連通路が開口する内壁面を有し、
前記吸入通路は、前記駆動軸に形成された第1吸入通路と、前記シリンダブロックに形成された第2吸入通路とを有し、
前記第1吸入通路は、前記吸入領域と前記第2連通路とに連通し、
前記第2吸入通路は、一端側が前記吸入領域に開口し、他端側が前記第2連通路と連通可能に前記内壁面に開口していることを特徴とするピストン式圧縮機。
前記第1吸入通路は、前記駆動軸内で前記軸心方向に延び、前記第2連通路に連通する軸路と、前記駆動軸の径方向に延び、前記斜板室と前記軸路とを連通する径路とを有している。
前記軸孔は、前記軸心方向の一方側に配置された一方側軸孔と、前記軸心方向の他方側に配置された他方側軸孔とを有し、
前記ピストンは、前記一方側シリンダボア内に一方側圧縮室を形成する一方側ヘッドと、前記他方側シリンダボア内に他方側圧縮室を形成する他方側ヘッドとを有し、
前記第1連通路は、前記一方側シリンダボアに連通する一方側第1連通路と、前記他方側シリンダボアに連通する他方側第1連通路とからなり、
前記一方側軸孔は、前記一方側第1連通路が開口する一方側内壁面を有し、
前記他方側軸孔は、前記他方側第1連通路が開口する他方側内壁面を有し、
前記第2連通路は、前記一方側第1連通路と連通し、
前記第1吸入通路は、前記駆動軸の径方向に延び、前記軸路と前記他方側第1連通路とを連通する連絡路を有し、
前記第2吸入通路は、一端側が前記斜板室に開口し、他端側が前記第2連通路と連通可能に前記一方側内壁面に開口する一方側第2吸入通路と、
一端側が前記連絡路と連通可能に前記他方側内壁面に開口し、他端側が前記斜板室に開口する他方側第2吸入通路とからなる。
前記駆動軸には、前記軸路と連通するとともに前記一方側軸孔内に開口し、前記第1移動体が配置される案内窓が形成され、
前記第1移動体によって前記一方側第1連通路と前記第2連通路とが連通され、
前記駆動軸によって前記一方側第1連通路と前記第2連通路とが非連通とされ、
前記第2移動体には、前記軸路内に位置し、前記一方側圧縮室から前記吐出室に吐出される冷媒の流量が減少すれば、前記第1吸入通路によって前記斜板室内から前記他方側圧縮室内に吸入させる冷媒の流量を減少させる吸入弁体が接続されている。
3…駆動軸
3c…第1保持溝(保持溝)
5…固定斜板
7…ピストン
7a…第1ヘッド(他方側ヘッド)
7b…第2ヘッド(一方側ヘッド)
8…第1弁形成プレート(吐出弁)
9…第2弁形成プレート(吐出弁)
11…移動体
11a…第1移動体
11b…第2移動体
12…吸入通路
13…吸入弁体
15…制御弁
21…第1シリンダブロック(シリンダブロック)
21a~21e…第1シリンダボア(他方側シリンダボア)
22…第2シリンダブロック(シリンダブロック)
22a~22e…第2シリンダボア(一方側シリンダボア)
23…第2軸孔(軸孔、他方側軸孔)
24a~24e…フロント側連通路(他方側第1連通路)
25…第3軸孔(軸孔、一方側軸孔)
26a~26e…リヤ側連通路(一方側第1連通路)
27…第1吐出室(吐出室)
28…制御圧室
29…第2吐出室(吐出室)
30…第1吸入通路
31…斜板室(吸入領域)
33…軸路
35…径路
37…連絡路
39…案内窓
41a…第1シールリング(第1封止部材)
41b…第2シールリング(第2封止部材)
43a~43e…第1圧縮室(他方側圧縮室)
45a~45e…第2圧縮室(一方側圧縮室)
47…移動体通路(第2連通路)
61a~61e…フロント側吸入通路(第2吸入通路、他方側第2吸入通路)
63a~63e…リヤ側吸入通路(第2吸入通路、一方側第2吸入通路)
173…第1軸孔(軸孔)
231…内壁面(他方側内壁面)
240…支持突起(延在部)
242…嵌合部材(延在部)
251…内壁面(一方側内壁面)
O…軸心
Claims (7)
- 複数のシリンダボアが形成されたシリンダブロックを有し、軸孔と、吐出室と、前記吐出室よりも低圧をなす吸入領域とが形成されたハウジングと、
前記軸孔内に回転可能に支承された駆動軸と、
前記駆動軸の回転によって前記ハウジング内で回転可能であり、前記駆動軸に垂直な平面に対する傾斜角度が一定である固定斜板と、
前記各シリンダボア内に圧縮室を形成し、前記固定斜板に連結されるピストンと、
前記吸入領域内の冷媒を前記圧縮室内に吸入させる吸入通路と、
前記圧縮室内の冷媒を前記吐出室に吐出させる吐出弁と、
前記駆動軸に設けられて前記軸孔内に位置し、前記駆動軸と一体回転するとともに、制御圧力に基づいて前記駆動軸の軸心方向に前記駆動軸に対して移動可能である移動体と、
前記制御圧力を制御する制御弁とを備え、
前記シリンダブロックには、前記シリンダボアに連通する第1連通路が形成され、
前記移動体には、前記駆動軸の回転に伴い間欠的に前記第1連通路と連通する第2連通路が形成され、
前記移動体の前記軸心方向の位置に応じて、前記圧縮室から前記吐出室に吐出される冷媒の流量が変化するピストン式圧縮機であって、
前記軸孔は、前記第1連通路が開口する内壁面を有し、
前記ハウジングは、前記駆動軸の軸心方向の一方側に配置され、前記吐出室及び前記制御圧室が形成されるとともに、前記吐出弁を介して前記シリンダブロックと前記軸心方向に接合される第1ハウジングを有し、
前記シリンダブロックは、前記軸心方向で前記制御圧室内に延びるとともに前記軸孔の一部が形成された延在部を有し、
前記吸入通路は、前記駆動軸に形成された第1吸入通路を有し、
前記第1吸入通路は、前記駆動軸内で前記軸心方向に延び、前記第2連通路に連通するとともに前記制御圧室に連通する軸路と、前記駆動軸の径方向に延び、前記斜板室と前記軸路とを連通する径路とを有し、
前記移動体は、前記第2連通路が形成された第1移動体と、第1移動体と連結されて前記軸路内に位置し、前記制御圧室と対向しつつ、前記軸路内を前記軸心方向に移動可能な第2移動体とを有し、
前記駆動軸には、環状に形成されて前記延在部内に位置し、前記軸心周りに回転する駆動軸によって前記内壁面を前記軸心周りに摺動しつつ、前記吸入領域と前記制御圧室との間を封止する第1封止部材が設けられ、
前記駆動軸の前記外周面には、環状に形成されて前記延在部内に位置し、前記第1封止部材を収容して保持する保持溝が形成され、
前記保持溝は、前記軸心方向において前記吐出弁よりも前記制御圧室側に配置されていることを特徴とするピストン式圧縮機。 - 前記吸入通路は、前記シリンダブロックに形成された第2吸入通路を有し、
前記第2吸入通路は、一端側が前記吸入領域に開口し、他端側が前記第2連通路と連通可能に前記内壁面に開口している請求項1記載のピストン式圧縮機。 - 前記吸入領域は、前記固定斜板を回転可能に収容する斜板室である請求項2記載のピストン式圧縮機。
- 前記シリンダボアは、前記軸心方向の一方側に配置された一方側シリンダボアと、前記軸心方向の他方側に配置された他方側シリンダボアとからなり、
前記軸孔は、前記軸心方向の一方側に配置された一方側軸孔と、前記軸心方向の他方側に配置された他方側軸孔とを有し、
前記ピストンは、前記一方側シリンダボア内に一方側圧縮室を形成する一方側ヘッドと、前記他方側シリンダボア内に他方側圧縮室を形成する他方側ヘッドとを有し、
前記第1連通路は、前記一方側シリンダボアに連通する一方側第1連通路と、前記他方側シリンダボアに連通する他方側第1連通路とからなり、
前記一方側軸孔は、前記一方側第1連通路が開口する一方側内壁面を有し、
前記他方側軸孔は、前記他方側第1連通路が開口する他方側内壁面を有し、
前記第2連通路は、前記一方側第1連通路と連通し、
前記第1吸入通路は、前記駆動軸の径方向に延び、前記軸路と前記他方側第1連通路とを連通する連絡路を有し、
前記第2吸入通路は、一端側が前記斜板室に開口し、他端側が前記第2連通路と連通可能に前記一方側内壁面に開口する一方側第2吸入通路と、
一端側が前記連絡路と連通可能に前記他方側内壁面に開口し、他端側が前記斜板室に開口する他方側第2吸入通路とからなり、
前記延在部には、前記一方側軸孔の一部が形成され、
前記第1封止部材は、前記一方側内壁面を前記軸心周りに摺動する請求項3記載のピストン式圧縮機。 - 前記駆動軸には、前記軸路と連通するとともに前記一方側軸孔内に開口し、前記第1移動体が配置される案内窓が形成され、
前記第1移動体によって前記一方側第1連通路と前記第2連通路とが連通され、
前記駆動軸によって前記一方側第1連通路と前記第2連通路とが非連通とされ、
前記第2移動体には、前記軸路内に位置し、前記一方側圧縮室から前記吐出室に吐出される冷媒の流量が減少するとともに前記第1吸入通路によって前記斜板室内から前記他方側圧縮室内に吸入させる冷媒の流量を減少させる吸入弁体が接続されている請求項4記載のピストン式圧縮機。 - 前記第2移動体には、前記斜板室と前記制御圧室との間を封止する第2封止部材が設けられ、
前記第2封止部材は、前記一方側圧縮室から前記吐出室に吐出される冷媒の流量が最大であるとき、前記軸心方向において、前記第1封止部材よりも前記案内窓に近い側に位置する請求項5記載のピストン式圧縮機。 - 前記一方側第1連通路は複数であり、
前記各一方側第1連通路は、前記シリンダブロックに対して周方向に配置され、
前記各一方側第1連通路同士における周方向の間隔は、前記一方側シリンダ側から前記一方側内壁面側に向かって次第に小さくなり、
前記一方側軸孔内における前記各一方側第1連通路から前記第1封止部材までの前記軸心方向の距離は、前記各一方側第1連通路同士における周方向の最小間隔よりも長い請求項4乃至6のいずれか1項記載のピストン式圧縮機。
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