WO2005024234A1 - 斜板式圧縮機 - Google Patents
斜板式圧縮機 Download PDFInfo
- Publication number
- WO2005024234A1 WO2005024234A1 PCT/JP2004/011374 JP2004011374W WO2005024234A1 WO 2005024234 A1 WO2005024234 A1 WO 2005024234A1 JP 2004011374 W JP2004011374 W JP 2004011374W WO 2005024234 A1 WO2005024234 A1 WO 2005024234A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- swash plate
- peripheral portion
- outer peripheral
- thickness
- swash
- Prior art date
Links
Classifications
-
- 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
- F04B27/1063—Actuating-element bearing means or driving-axis bearing means
-
- 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
- F04B27/0882—Pistons piston shoe retaining means
-
- 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
- F04B27/0886—Piston shoes
-
- 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
-
- 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
-
- 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
-
- 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
- F05B2210/12—Kind or type gaseous, i.e. compressible
-
- 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
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S417/00—Pumps
Definitions
- the present invention relates to, for example, a swash plate compressor that forms a refrigeration circuit and compresses refrigerant gas.
- a drive shaft 91 is rotatably supported by the housing 85, and a rotor 87 is fixed to the drive shaft 91 so as to be rotatable.
- a swash plate 92 is supported on the drive shaft 91 so as to be slidable and tiltable in the direction of the axis L.
- a hinge mechanism 88 is interposed between the rotor 87 and the swash plate 92.
- a single-headed piston 94 is moored.
- the sheaves 93A and 93B are perpendicular to a sliding contact surface 93b that passes through the axis S (the center of curvature P of the sliding hemispherical surface 93a and slides with the swash plate 92) according to the relative rotation with the swash plate 92. Rotation).
- the rotation of the shafts 93A and 93B about the axis S is, as a whole, in one direction around the shaft S with respect to the shafts 93A and 93B due to the difference in peripheral speed between the inner and outer peripheries of the swash plate 92. This is performed in a state equivalent to applying rotational force to
- the swash plate compressor shown in FIG. 11 has a configuration in which the shoes 93A and 93B slide directly on the swash plate 92. Therefore, the slides 93A and 93B had to wastefully perform the rotational movement about the axis S by sliding based on the relative rotation with the swash plate 92. Therefore, there is a problem in that mechanical loss is particularly large in a sliding portion between the piston 94 and the shoe 93B on the side receiving the compression reaction force, and problems such as seizure occur in the sliding portion. .
- the swash plate 92 and the rolling bearing are interposed in a limited space between the swash plate 93A and the sew 93B, the swash plate 92 becomes thin and a predetermined strength cannot be secured. There is. Further, in the piston 94 near the top dead center position (compression stroke), the load force from the shaft 93B which receives a large compression reaction force is concentrated on the specific rolling element in the rolling bearing. Therefore, there is a problem that the durability of the rolling element which is small enough to be disposed in the limited space between the shoe 93A and the shoe 93B (in other words, the strength is low) becomes severe.
- a step portion 90a is provided in the center of the rear surface of the first swash plate 90 (the surface facing the right side in the drawing) in an annular shape.
- an annular second swash plate 95 is formed outside the stepped portion 90a through a support hole 95a formed through the center portion with respect to the first swash plate 90. And are supported so as to be relatively rotatable.
- the outer peripheral portion of the second swash plate 95 is slidably provided between the first swash plate 90 and the shoe 93B between the first swash plate 90 and the shoe 93B.
- the rotational movement of the show 93B about the axis S due to the relative rotation between the second swash plate 95 and the show 93B can be suppressed, and the above-described mechanical loss and occurrence of defects can be suppressed. it can.
- the thickness of the first swash plate 90 (in other words, the thickness of the first swash plate 90 which is merely interposed between the thin swash plate 95 and the first swash plate 90). If the piston 93 near the top dead center position (compression stroke) receives a large compression reaction force, the load from the shaft 93B, which receives a large compression reaction force, is distributed over a large area of the second swash plate 95. As a result, the durability of the second swash plate 95 can be improved.
- Patent Document 1 JP-A-8-28447 (Page 3, FIG. 1)
- Patent Document 2 JP-A-8-338363 (Page 4, FIG. 1)
- An object of the present invention is to provide a swash plate compressor capable of improving the slip between the first swash plate and the second swash plate.
- an invention is directed to a driving shaft, wherein a first swash plate is integrally rotatably connected to the drive shaft, and the first swash plate supports a second swash plate.
- a piston is moored to the second swash plate via a first shoe in contact with the first swash plate and a second shoe on a side receiving a compression reaction force in contact with the second swash plate.
- a swash plate type compressor in which the piston is reciprocated linearly by the rotation of the first swash plate in association with the rotation of a drive shaft to compress the refrigerant gas.
- a thrust bearing that supports the second swash plate so as to be rotatable relative to the first swash plate is disposed between an outer peripheral portion of the first swash plate and an outer peripheral portion of the second swash plate.
- a swash plate compressor in which a radial bearing that supports the second swash plate so as to be rotatable relative to the first swash plate is disposed between an inner peripheral portion and an inner peripheral portion of the second swash plate. I will provide a.
- the "radial bearing” refers to a bearing having a configuration capable of appropriately receiving a radial load acting on the second swash plate
- the "thrust bearing” refers to the second swash plate.
- the radial bearing may have a configuration capable of receiving not only a radial load but also a thrust load
- the thrust bearing may have a configuration capable of receiving not only a thrust load but also a radial load.
- the first swash plate is provided with a supporting portion that rotatably supports the second swash plate via the radial bearing, and the first swash plate supports the second swash plate.
- An accommodation groove for accommodating a part of the radial bearing is formed around the base of the part. Therefore, the bearing can be arranged closer to the base side of the support portion, and the degree of projection of the swash plate force of the bearing, that is, the support portion can be reduced, and the swash plate can be downsized.
- a coefficient of friction between the first swash plate and the second swash plate is set to be smaller than a coefficient of friction between the second swash plate and the second swash plate. . Therefore, the sliding between the second swash plate and the first swash plate can be further improved.
- the thickness of the outer peripheral portion of the second swash plate is 1/3 or more of the thickness of the outer peripheral portion of the first swash plate, and the thickness of the first swash plate is It is thinner than the outer peripheral plate thickness.
- the space between the first and second shoes is limited.
- increasing the thickness of the outer peripheral portion of the first swash plate requires reducing the thickness of the outer peripheral portion of the second swash plate, and conversely, increasing the outer peripheral portion of the second swash plate. If the thickness is increased, it is necessary to reduce the thickness of the outer peripheral portion of the first swash plate. From the standpoint of receiving the compression reaction force, it is necessary to increase the thickness of the outer peripheral part as much as possible for both the first and second swash plates to secure the strength, but power is transmitted from the drive shaft.
- the securing of the thickness of the outer peripheral portion of the first swash plate to be reached should be given priority over the securing of the thickness of the outer peripheral portion of the second swash plate, which only needs to slide on the first swash plate.
- the thickness of the outer peripheral portion of the second swash plate is set to be at least half the thickness of the outer peripheral portion of the first swash plate and smaller than the outer peripheral portion of the first swash plate. That is the thing.
- the second swash plate has an annular shape, and the second swash plate has an inner peripheral portion supported by the radial bearings having a thickness equal to that of the first swash plate.
- the thickness is larger than the thickness of the outer peripheral portion interposed between the second shoe. Therefore, the support of the second swash plate by the bearing is stabilized by the thick inner peripheral portion, and the sliding between the second swash plate and the first swash plate can be further improved.
- the thickness of the outer peripheral portion of the second swash plate is smaller than the thickness of the outer peripheral portion of the first swash plate, and the inner peripheral portion of the second swash plate has a smaller thickness.
- the thickness of the portion is greater than the thickness of the outer peripheral portion of the first swash plate.
- the thin outer peripheral portion of the second swash plate facilitates securing the thickness of the outer peripheral portion of the first swash plate which is stricter in strength than the second swash plate. Further, in the second swash plate, the thickness of the inner peripheral portion is greater than the thickness of the outer peripheral portion of the first swash plate. Therefore, the support of the second swash plate by the radial bearing is further stabilized.
- the inner peripheral portion of the second swash plate has a cylindrical first protruding portion protruding from the first swash plate and a protruding portion opposite to the first swash plate.
- the second swash plate has a thickness greater than that of the outer peripheral portion by providing the cylindrical second protrusion, and the outer diameter of the second protrusion is the first protrusion. It is smaller than the outer diameter of the shape.
- the radial bearing is formed of a rolling bearing, and a contact hole is used as a rolling element of the radial bearing.
- a rolling bearing using a roller as a rolling element has excellent load resistance compared to, for example, a case using a ball as a rolling element. This is This leads to a reduction in the size of the radial bearing and, consequently, the size of the swash plate compressor.
- the thrust bearing is formed of a rolling bearing, and a race is interposed between a rolling element of the thrust bearing and the first swash plate. Can be rotated relative to.
- a part of the first swash plate (corresponding to a piston near the top dead center position). Large compressive reaction force is applied to the part), and there is a problem that the part is locally worn and deteriorated.
- a race is interposed between the rolling element and the first swash plate, and a large compressive reaction force acting on the rolling element reduces the surface pressure through the race to reduce the surface pressure. Since the first swash plate acts on the swash plate, it is possible to suppress the first swash plate from being locally worn and deteriorated. Further, in a race that rotates relative to the first swash plate, portions where a large compression reaction force acts via the rolling elements are sequentially switched, and it is possible to prevent the race from being locally worn and deteriorated.
- a locking portion protrudes from the outer peripheral portion of the first swash plate toward the second swash plate, and the race comes into contact with the locking portion. Are locked to the first swash plate on the radially outer side.
- the race is attached to the first swash plate.
- the lubricating oil refrigeration oil
- the engagement of the lubricating oil between the first swash plate and the race is hindered by the locking portion.
- the locking portion has an annular shape. Therefore, the locking of the race by the locking portion is performed stably, and the sliding between the race and the first swash plate is further improved.
- the inner peripheral portion of the second swash plate is provided with a cylindrical protruding portion protruding on a side opposite to the first swash plate, so that the inner peripheral portion of the second swash plate has a larger diameter than the outer peripheral portion.
- the protruding portion is provided with an inclined surface (chamfer) at the outer peripheral angle of the tip end surface. The inclined surface (chamfer) reduces the weight of the second swash plate.
- a lightening hole is formed through the second swash plate in a plate thickness direction.
- the lightening holes reduce the weight of the second swash plate.
- At least one of a front surface and a rear surface of the second swash plate is provided with a lightening recess.
- the lightening recess reduces the weight of the second swash plate.
- At least one of the first swash plate and the second swash plate is provided with an oil introduction passage for introducing oil from outside between the first swash plate and the second swash plate. Has been. Therefore, the slippage between the second swash plate and the first swash plate can be further improved by the presence of the oil.
- the oil introduction passage includes a through hole formed through the first swash plate or the second swash plate.
- the swash plate compressor is a variable displacement swash plate compressor in which the displacement is changed by changing the inclination angles of the first and second swash plates.
- the gas is a refrigerant gas used in a refrigeration circuit, and the refrigerant gas is made of carbon dioxide.
- the pressure in the refrigeration circuit is much higher than when a chlorofluorocarbon refrigerant (for example, R134a) is used. Therefore, also in the swash plate type compressor, the compression reaction force acting on the piston increases, and the pressing force of the second swash plate against the first swash plate increases.
- the arrangement of a thrust bearing and a radial bearing between the first swash plate and the second swash plate to facilitate slipping between the first and second swash plates is particularly difficult. It is valid.
- FIG. 1 is a longitudinal sectional view of a swash plate type compressor according to a first embodiment of the present invention.
- FIG. 2 is an enlarged view of a main part of FIG. 1.
- FIG. 3 is a partial sectional view showing a second embodiment of the present invention.
- FIG. 4 is a longitudinal sectional view of a variable displacement swash plate type compressor according to a third embodiment of the present invention.
- FIG. 5 is an enlarged view of a main part of FIG. 4, in which the first and second swash plates are not in section (partially broken), and a part of the first and second shows are in section.
- FIG. 6 is an enlarged view of a main part showing a swash plate structure according to a fourth embodiment of the present invention.
- FIG. 7 is an enlarged view of a main part showing a swash plate structure according to a fifth embodiment of the present invention.
- FIG. 8 is a rear view of the second swash plate shown in FIG. 7.
- FIG. 9 is an enlarged view of a main part showing a swash plate structure according to a sixth embodiment of the present invention.
- FIG. 10 is an essential part enlarged view showing a swash plate structure according to a seventh embodiment of the present invention.
- FIG. 11 is a longitudinal sectional view of a conventional variable displacement swash plate compressor.
- FIG. 12 is a partial sectional view showing a conventional technique.
- FIG. 1 is a longitudinal sectional view of a variable capacity swash plate compressor (hereinafter simply referred to as a compressor 10).
- a compressor 10 variable capacity swash plate compressor
- the left side is the front of the compressor 10 and the right side is the rear of the compressor.
- the housing of the compressor 10 includes a cylinder block 11, a front bar and a housing 12 joined and fixed to the front end of the cylinder block 11, and a valve and port at the rear end of the cylinder block 11. And a rear housing 14 joined and fixed via a formed body 13.
- a crank chamber 15 is defined between the cylinder block 11 and the front housing 12.
- a drive shaft 16 is rotatably disposed between the cylinder block 11 and the front housing 12 so as to pass through the crank chamber 15.
- the drive shaft 16 is operatively connected via a power transmission mechanism PT of an engine E force clutchless type (constant transmission type) which is a traveling drive source of the vehicle. Therefore, during the operation of the engine E, the drive shaft 16 is constantly rotated by receiving the power supply from the engine E.
- a rotor 17 is fixed to the drive shaft 16 in the crank chamber 15 so as to be able to rotate.
- a first swash plate 18 having a substantially disk shape is accommodated.
- the first swash plate 18 is made of an iron-based metal material (pure iron or iron alloy).
- a through hole 18a is formed through the center of the first swash plate 18.
- the drive shaft 16 is inserted into the through hole 18a of the first swash plate 18.
- the first swash plate 18 is connected to the drive shaft 16 through the through hole 18a. It is slidably and tiltably supported.
- a hinge mechanism 19 is interposed between the rotor 17 and the first swash plate 18.
- the hinge mechanism 19 includes two rotor-side protrusions 41 (one of which is not shown in the drawing) projecting from the rear surface of the rotor 17 and a rotor And a swash plate side projection 42 protruding toward the 17th side.
- the swash plate-side projection 42 has its tip side inserted between the two data-side projections 41. Therefore, the rotational force of the rotor 17 is transmitted to the first swash plate 18 via the rotor-side protrusion 41 and the swash-plate-side protrusion 42.
- a cam portion 43 is formed at the base of the rotor-side projection 41.
- a cam surface 43a is formed on a rear end surface of the cam portion 43 facing the first swash plate 18.
- the tip of the swash plate side projection 42 is slidably abutted against the cam surface 43a of the force portion 43. Therefore, the hinge mechanism 19 guides the tilting of the first swash plate 18 by moving the tip of the swash plate side projection 42 on the cam surface 43a of the cam portion 43 in the direction of coming and going with respect to the drive shaft 16.
- a plurality of cylinder bores 22 are formed in the cylinder block 11 around the axis L of the drive shaft 16 at equal angular intervals in the front-rear direction (lateral direction on the paper).
- the single-headed piston 23 is accommodated in each cylinder bore 22 so as to be movable in the front-rear direction.
- the front and rear openings of the cylinder bore 22 are closed by the front end face of the valve port forming body 13 and the piston 23, and a compression chamber 24 whose volume changes in accordance with the movement of the piston 23 in the front and rear direction is defined in the cylinder bore 22. Have been.
- the piston 23 has a cylindrical head 37 inserted into the cylinder bore 22 and a neck 38 located in the crank chamber 15 outside the cylinder bore 22 and connected in the front-rear direction.
- the head 37 and the neck 38 are made of an aluminum-based metal material (pure aluminum or aluminum alloy).
- a pair of shoe seats 38a are recessed.
- a first show 25A and a second show 25B which form a hemisphere, are provided.
- the first shoe 25A and the second shoe 25B are made of an iron-based metal material.
- the “hemisphere” refers to one having a part of a spherical surface that does not mean only a half of a sphere.
- the first shoe 25A and the second shoe 25B are each spherically received by a shroud 38a with a hemispherical surface 25a.
- Hemisphere 25a of first show 25A and hemisphere of second show 25B 2 5a exists on the same spherical surface centered on the curvature center point P of each hemispheric surface 25a.
- Each piston 23 is moored to the outer periphery of the first swash plate 18 and the second swash plate 51 via the first shower 25A and the second shower 25B. Therefore, when the first swash plate 18 rotates by the rotation of the drive shaft 16, the piston 23 reciprocates linearly in the front-rear direction.
- a suction chamber 26 and a discharge chamber 27 are separately formed between the valve / port forming body 13 and the lary housing 14.
- the valve port forming body 13 is formed with a suction port 28 and a suction valve 29 so as to be located between the compression chamber 24 and the suction chamber 26.
- a discharge port 30 and a discharge valve 31 are formed in the valve / port forming body 13 so as to be located between the compression chamber 24 and the discharge chamber 27.
- Carbon dioxide is used as a refrigerant in the refrigeration circuit.
- Refrigerant gas introduced into the suction chamber 26 from an external circuit (not shown) is sucked into the compression chamber 24 via the suction port 28 and the suction valve 29 by moving from the top dead center position to the bottom dead center position of each piston 23. Is done.
- the refrigerant gas sucked into the compression chamber 24 is compressed to a predetermined pressure by moving from the bottom dead center position of the piston 23 to the top dead center position side, and is discharged through the discharge port 30 and the discharge valve 31 to the discharge chamber 2. It is discharged to 7.
- the refrigerant gas in the discharge chamber 27 is led to an external circuit.
- a bleed passage 32 In the housing of the compressor 10, a bleed passage 32, an air supply passage 33, and a control valve 34 are provided.
- the bleed passage 32 connects the crank chamber 15 and the suction chamber 26.
- the air supply passage 33 connects the discharge chamber 27 and the crank chamber 15.
- a well-known control valve 34 composed of a solenoid valve is provided.
- the opening of the control valve 34 By adjusting the opening of the control valve 34 by external power supply control, the amount of high-pressure discharge gas introduced into the crank chamber 15 through the air supply passage 33 and the amount of crank through the bleed passage 32 The balance with the amount of gas led out from the chamber 15 is controlled, and the internal pressure of the crank chamber 15 is determined. The difference between the internal pressure of the crank chamber 15 and the internal pressure of the compression chamber 24 is changed in accordance with the change in the internal pressure of the crank chamber 15, and the inclination angle of the first swash plate 18 is changed. The discharge capacity of the machine 10 is adjusted.
- a support portion 39 having a substantially cylindrical shape is provided at the center of the rear surface of the first swash plate 18 so as to surround the drive shaft 16. .
- An annular second swash plate 51 is disposed outside the support portion 39 of the first swash plate 18 in a state where the support portion 39 is passed through a support hole 51a formed through the center of the second swash plate 51.
- a ball bearing 52 as a bearing is interposed between the outer peripheral surface of the support portion 39 and the inner peripheral surface of the support hole 51a of the second swash plate 51.
- the ball bearing 52 is a radial bearing, and the radial load of the second swash plate 51 is supported by the first swash plate 18 (support portion 39) via the ball bearing 52.
- the ball bearing 52 includes a substantially cylindrical inner ring 52a, a substantially cylindrical outer ring 52b disposed outside the inner ring 52a, and a rolling element interposed between the inner ring 52a and the outer ring 52b. It comprises a plurality of balls 52c as elements.
- an accommodation groove 18b is formed in an annular region around the base of the support portion 39.
- the ball bearing 52 is externally fitted to the support portion 39 such that a part of each of the inner ring 52a and the outer ring 52b is located in the accommodation groove 18b.
- a circlip 53 is snap-engaged with the outer peripheral surface of the distal end of the support portion 39.
- the ball bearing 52 is prevented from coming off from the support portion 39 by the inner ring 52 a contacting the circlip 53.
- a ball bearing 52 is press-fitted into a support hole 51a of the second swash plate 51 with an outer ring 52b. Accordingly, the second swash plate 51 can rotate integrally with the outer ring 52b of the ball bearing 52, that is, can rotate relative to the support portion 39 (the first swash plate 18).
- the outer peripheral portion 51b of the second swash plate 51 is provided between the first swash plate 18 and the second shoe 25B on the compression chamber 24 side (the side receiving the compression reaction force). It is slidably mounted on the shoe 25B.
- the plate thickness of the inner peripheral portion 51c directly receiving the support of the ball bearing 52 is larger than the plate thickness of the outer peripheral portion 51b interposed between the first swash plate 18 and the second shoe 25B. I'm familiar.
- the second swash plate 51 has a surface 51b-1 on the outer peripheral portion 51b side and a region 51c-l on the inner peripheral portion 51c side flush with the front surface sliding with the first swash plate 18. Have been. Therefore, on the rear surface of the second swash plate 51, the region 51c_2 on the inner peripheral portion 51c side is moved to the outer peripheral portion 51 which is slid with the second shoe 25B.
- the inner swash plate 51 has an inner peripheral portion 51c having a greater thickness than the outer peripheral portion 51b by being displaced in parallel behind the region 51b-2 on the b side.
- the region 51b_2 and the region 51c-2 are smoothly connected by an inclined surface in order to reduce stress concentration on a connecting portion between the two.
- the second swash plate 51 As a base material of the second swash plate 51, mild steel such as SPC (polishing material) and SPHC (pickling material) is used. On the front surface of the second swash plate 51, that is, on a region 51b_l on the outer peripheral portion 51b side and a region 51c-l on the inner peripheral portion 51c side, a coating 54 made of a solid lubricant is formed. Only the region 51b-1 in the enlarged circle is exaggerated in film thickness). Examples of the solid lubricant include molybdenum disulfide and a fluorine resin such as PTFE (polytetrafluoroethylene).
- a plurality of oil grooves 51d are formed on the front surface (region 51b_l and region 51c_l) of the second swash plate 51 radially around the center of the annular shape of the second swash plate 51.
- the oil groove 51d functions as an oil introduction passage for introducing oil (refrigeration machine oil) existing in the crank chamber 15 to a sliding portion between the first swash plate 18 and the second swash plate 51.
- the sliding portion between the first swash plate 18 and the second swash plate 51 is formed by the second shoe 25B and the second shoe 25B due to the interposition of the coating 54 made of a solid lubricant and the introduction of oil through the oil groove 51d.
- the friction coefficient is smaller than the sliding part with the swash plate 51.
- the rotation speed of the second swash plate 51 is lower than the rotation speed of the first swash plate 18. Therefore, the relative rotation speed between the second swash plate 51 and the second swash plate 25B (the relative rotation speed of the second swash plate 51 with respect to the second swash plate 25B) 1 The relative rotation speed between the second swash plate 25B and the first swash plate 18 The speed is lower than the speed (the relative rotation speed of the first swash plate 18 with respect to the second shoe 25B).
- the present embodiment having the above configuration has the following effects.
- the second swash plate 51 is rotatable relative to the first swash plate 18 via a ball bearing 52. It is supported. Accordingly, slippage is likely to occur between the first swash plate 18 and the second swash plate 51, and the relative rotation speed between the second swash plate 51 and the second swash plate 25B (the second swash plate 51 with respect to the second swash plate 25B). It is easy to make the relative rotation speed) lower than the relative rotation speed between the second shoe 25B and the first swash plate 18 (the relative rotation speed of the first swash plate 18 with respect to the second shoe 25B). Therefore, the effect of the provision of the second swash plate 51 (reduction of mechanical loss, etc.) can be sufficiently exhibited.
- the piston 23 is of a single-head type. Therefore, since the second shoe 25B on the side receiving the compression reaction force is pressed more strongly against the piston 23 than the first shoe 25A on the opposite side, the sliding environment between the second shoe 25B and the piston 23 is increased. Is tough.
- interposing the second swash plate 51 between the first swash plate 18 and the second shoe 25B on the side receiving the compression reaction force is advantageous in that the second swash plate 51 is provided. This is particularly effective for reducing mechanical loss.
- This embodiment is embodied in the compressor 10 constituting the refrigeration circuit, and carbon dioxide is used as the refrigerant of the refrigeration circuit.
- carbon dioxide refrigerant When a carbon dioxide refrigerant is used, the pressure in the refrigeration circuit is much higher than when a chlorofluorocarbon refrigerant (for example, R134a) is used. Therefore, also in the compressor 10, the compression reaction force acting on the piston 23 increases, and the pressing force of the second swash plate 51 against the first swash plate 18 increases.
- the present invention is embodied to easily cause slippage between the first swash plate 18 and the second swash plate 51.
- the second swash plate 51 has a plate thickness of the inner peripheral portion 51c supported by the ball bearing 52, and a thickness of the outer peripheral portion 51b interposed between the first swash plate 18 and the second shoe 25B. It is larger than the plate thickness. Therefore, the support of the second swash plate 51 by the ball bearing 52 is stabilized by the thick inner peripheral portion 51c, and the sliding between the second swash plate 51 and the first swash plate 18 can be further improved.
- press fitting is employed for fixing the second swash plate 51 and the ball bearing 52 (outer ring 52b). Therefore, increasing the thickness of the inner peripheral portion 51c of the second swash plate 51 into which the ball bearing 52 is press-fitted leads to an improvement in the durability of the inner peripheral portion 51c which is directly subjected to the stress caused by the press-fitting.
- the piston 23 becomes larger.
- the embodiment in which the second swash plate 51 is interposed between the first swash plate 18 and the second shoe 25B can be realized while suppressing the formation of the swash plate.
- An increase in the size of the neck portion 38 of the piston 23 leads to an increase in the body diameter of the compressor 10 (the cross-sectional diameter of the housing of the compressor 10).
- the diameter of the head 37 of the piston 23 tends to be smaller than that of a compressor in a refrigeration circuit using a chlorofluorocarbon refrigerant.
- the large size of the compressor directly leads to the large size of the compressor 10 (body diameter).
- the outer peripheral portion 51b of the second swash plate 51 is thicker than the case of FIG. 1, the outer peripheral portion of the first swash plate 18 is made thinner or the first and second showers 25A and 25B It is necessary to reduce the size of the sphere (reducing the area of the hemisphere 25a from the embodiment of FIG. 1), or to increase the radius of the virtual sphere where the hemisphere 25a of the first show 25A and the second show 25B exists.
- reducing the thickness of the outer peripheral portion of the first swash plate 18 and reducing the size of the first shoe 25A and the second shoe 25B are not preferable because the respective durability is reduced. Therefore, the radius of the virtual sphere where the hemispherical surface 25a of the first shoe 25A and the second shoe 25B exists must be increased to correspond, and the piston 23 (neck portion 38) becomes larger accordingly. .
- the area 51c-2 on the inner peripheral part 51c side is made larger than the area 51b-2 on the outer peripheral part 51b side slid with the second shoe 25B.
- the inner peripheral portion 51c of the second swash plate 51 has a greater thickness than the outer peripheral portion 51b by being displaced parallel to the rear side. Therefore, the front surface of the second swash plate 51 that slides with the first swash plate 18 should be flush with the region 51b-1 on the outer peripheral portion 51b side and the region 51c-1 on the inner peripheral portion 51c side. This facilitates the processing, and a large sliding area with the first swash plate 18 can be secured. Therefore, it is possible to suppress the sliding wear of the first swash plate 18 and the second swash plate 51 while achieving the above-described effects (1-4).
- An accommodation groove 18b is formed around the base of the support portion 39 in the first swash plate 18, and a part of the ball bearing 52 is accommodated in the accommodation groove 18b. Therefore, the ball bearing 52 can be arranged close to the base of the support portion 39, and the degree of protrusion of the first swash plate 18 toward the ball bearing 52, that is, the rear portion of the support portion 39 can be reduced. The swash plate 18 can be reduced in size. This leads to downsizing of the compressor 10.
- the coefficient of friction between the first swash plate 18 and the second swash plate 51 is determined by the second shoe 25B and the second swash plate 51. Was set smaller than the coefficient of friction between. Therefore, the sliding between the second swash plate 51 and the first swash plate 18 can be further improved.
- the second swash plate 51 is provided with an oil groove 51d for introducing oil from the crank chamber 15 between the second swash plate 51 and the first swash plate 18. Therefore, the slippage between the second swash plate 51 and the first swash plate 18 can be further improved by the presence of the oil.
- a region 51b_1 on the outer peripheral portion 51b side and a region 51c-1 on the inner peripheral portion 51c side sliding with the first swash plate 18 are made of a solid lubricant.
- the coating 54 is formed.
- the coating 54 is a sliding bearing as a thrust bearing. Therefore, the sliding between the second swash plate 51 and the first swash plate 18 can be further improved.
- the oil groove 51d is omitted from the first embodiment, and a through hole 51e formed in the outer peripheral portion 51b of the second swash plate 51 in the plate thickness direction becomes an oil introduction passage. Is composed.
- the through hole 51e is provided so as to open a sliding portion between the outer peripheral portion 51b (region 51b_l) of the second swash plate 51 and the first swash plate 18 to the crank chamber 15.
- a plurality of through holes 51e are provided around the center of the ring of the second swash plate 51 at equal angular intervals.
- the through hole 51e shows a state in which the opening to the crank chamber 15 is closed by the second shoe 25B.
- the opening is not always closed by the second shoe 25B, but is shifted with respect to the second shoe 25B by the relative rotation of the second shower 25B and the second swash plate 51, so that the crank chamber 15 Will be open to the public.
- the first shoe 25A located on the hinge mechanism 19 side, that is, on the side opposite to the compression chamber 24, has a first sliding contact surface 25b opposite to the hemispheric surface 25a.
- the swash plate 18 is slidably abutted against the front surface of the outer peripheral portion 18-1.
- hinge machine The second shoe 25B on the side opposite to the structure 19, that is, on the compression chamber 24 side and receiving the compression reaction force has an outer peripheral portion 51-2 of the second swash plate 51 on a sliding contact surface 25b opposite to the hemispheric surface 25a. It is slidably abutted against the rear surface of the.
- the sliding surface 25b of the first shoe 25A has a middle-high shape whose central portion protrudes toward the first swash plate 18 (see FIG. 5; the middle-high shape is exaggerated in FIG. 5).
- the sliding surface 25b of the second shoe 25B has a planar shape.
- a radial bearing 52A composed of a rolling bearing is interposed between the support hole 51a and the inner peripheral surface of the support hole 51a.
- the radial bearing 52A has an outer race 52e attached to the inner peripheral surface of the support hole 51a in the second swash plate 51, and an inner race 52f attached to the outer peripheral surface of the support portion 39 in the first swash plate 18.
- a plurality of rollers 52g as rolling elements interposed between the outer race 52e and the inner race 52f.
- a thrust made of a rolling bearing is provided between the first shoe 25A and the second shoe 25B, between the outer peripheral portion 18-1 of the first swash plate 18 and the outer peripheral portion 51-2 of the second swash plate 51.
- Bearing 58 is interposed.
- the thrust bearing 58 has a plurality of rollers 58a as rolling elements, and the plurality of rollers 58a are rotatably held by a retainer 58b.
- an annular race 55 is interposed between the roller 58 a and the first swash plate 18.
- the race 55 is formed by subjecting a base material made of mild steel such as SPC to a carburizing heat treatment.
- the corners at both ends of the roller 58a are chamfered so that the roller 58a does not hit the second swash plate 51 and the race 55 to damage the second swash plate 51 and the race 55.
- an annular locking portion 18e protrudes from the outermost periphery of the outer peripheral portion 18-1 toward the second swash plate 51.
- the race 55 is arranged inside the locking portion 18e, and the race 55 is locked to the first swash plate 18 on the radially outer side by abutment of the outer peripheral edge thereof with the locking portion 18e.
- the race 55 is rotatable relative to the first swash plate 18 by being guided by the locking portion 18e.
- the second swash plate 51 is supported by the first swash plate 18 via the radial bearing 52A and the thrust bearing 58 so that the second swash plate 51 can rotate relative to the first swash plate 18 and can be tilted integrally. Has been done. Therefore, when the first swash plate 18 rotates, rolling occurs between the first swash plate 18 and the second swash plate 51 due to the action of the radial bearing 52A and the thrust bearing 58, causing slippage between the surfaces. The mechanical loss caused by the rolling is replaced by the mechanical loss caused by rolling, and the occurrence of mechanical loss in the compressor can be greatly suppressed.
- the thickness Y1 of the inner peripheral portion 51-1 which is supported by the radial bearing 52A in the second swash plate 51, is equal to the thickness Y2 of the outer peripheral portion 51-2, which is supported by the thrust bearing 58 in the second swash plate 51. It is thicker than it is. Specifically, the thickness Y2 of the outer peripheral portion 51-2 of the second swash plate 51 is not less than 1/3 of the thickness X of the outer peripheral portion 18-1 of the first swash plate 18 and the outer peripheral portion of the first swash plate 18. It is set thinner than the thickness X of 18-1. Further, the thickness Y1 of the inner peripheral portion 51-1 of the second swash plate 51 is larger than the thickness X of the outer peripheral portion 18-1 of the first swash plate 18.
- the inner peripheral portion 51-1 of the second swash plate 51 has a cylindrical first protruding portion 56 protruding from the first swash plate 18 and a protruding portion on the opposite side to the first swash plate 18.
- the second swash plate 51 has a greater thickness than the outer peripheral portion 51-2 of the second swash plate 51 by providing the cylindrical second projecting portion 57 (Y1> Y2).
- the first protrusion 56 and the second protrusion 57 are disposed coaxially with the support hole 51a, and the inner peripheral surfaces of the first protrusion 56 and the second protrusion 57 are formed on the inner periphery of the support hole 51a. Form a part of the surface.
- the outer diameter Z2 of the second protrusion 57 is smaller than the outer diameter Z1 of the first protrusion 56.
- a tapered inclined surface is provided at the outer peripheral angle 57a of the distal end surface.
- the support portion 39 is provided eccentrically toward the piston 23 A at the top dead center position with respect to the center axis Ml of the first swash plate 18. Accordingly, the second swash plate 51, the radial bearing 52A, and the thrust bearing 58 (including the race 55) are eccentric with respect to the first swash plate 18 toward the piston 23A at the top dead center position. Therefore, the center axis M2 of the second swash plate 51, the radial bearing 52A, and the thrust bearing 58 is the first axis corresponding to the piston 23A at the top dead center position with respect to the center axis Ml of the first swash plate 18. A slight amount (for example, 0.055 mm) is shifted parallel to the center point P side of the second shows 25A and 25B.
- a slight amount for example, 0.055 mm
- a portion corresponding to the piston 23A at the top dead center position and a portion located in front and rear of the portion in the circumferential direction are opposite to the second swash plate 51.
- An inclined surface (chamfered) is provided at the convex corner portion 18c.
- the inclined surface (chamfered) of the convex corner portion 18c is provided so that the portion corresponding to the piston 23A at the top dead center position becomes gradually smaller as it becomes circumferentially away from the largest portion.
- the inclined surface (chamfer) of the convex corner portion 18c is a quarter-peripheral region, with the portion corresponding to the piston 23A at the top dead center position as the middle. It is provided within the area.
- a portion corresponding to the piston 23 B at the bottom dead center position and a portion located in front and rear of the portion in the circumferential direction are provided with a convex portion on the second swash plate 51 side.
- An inclined surface (chamfer) is provided at the corner 18d.
- the inclined surface (chamfer) is provided so that a portion corresponding to the piston 23B at the bottom dead center position becomes gradually smaller as it is further away from the largest portion in the circumferential direction.
- the inclined surface (chamfer) of the convex corner portion 18d is provided within a quarter-peripheral region with a portion corresponding to the piston 23B located at the bottom dead center position as a middle region.
- the inclined surface (chamfer) of the convex corner portion 18d is provided with substantially the same size as the inclined surface (chamfer) of the convex corner portion 18c in consideration of the weight balance around the central axis Ml of the first swash plate 18. Have been.
- a second swash plate 51 is provided between the first shoe 25A and the second shoe 25B, between the outer peripheral portion 18-1 of the first swash plate 18 and the outer peripheral portion 51-2 of the second swash plate 51.
- a thrust bearing 58 that supports the plate 51 so as to be rotatable relative to the first swash plate 18 is provided.
- the second swash plate 51 is relatively rotated with respect to the first swash plate 18 between the inner peripheral portion (support portion 39) of the first swash plate 18 and the inner peripheral portion 51-1 of the second swash plate 51.
- a radial bearing 52A is provided for supporting as much as possible.
- the thickness Y2 of the outer peripheral portion 51-2 of the second swash plate 51 is not less than 1/3 of the thickness X of the outer peripheral portion 18-1 of the first swash plate 18 and the outer peripheral portion 18-2. -It is thinner than the thickness X of 1.
- the space between the first shoe 25A and the second shoe 25B is limited. In this limited space, if the thickness X of the outer peripheral portion 18-1 of the first swash plate 18 is increased, the thickness Y2 of the outer peripheral portion 51-2 of the second swash plate 51 needs to be reduced. 2 When the thickness Y2 of the outer peripheral portion 51-2 of the swash plate 51 is increased, 1 It is necessary to reduce the thickness X of the outer peripheral portion 18-1 of the swash plate 18.
- the first swash plate 18 and the second swash plate 51 are made as thick as possible in the outer peripheral portions 18-1 and 51-2 to secure the strength.
- Required Force In the first swash plate 18 to which power is transmitted from the drive shaft 16 the thickness X of the outer peripheral portion 18-1 can be ensured by sliding with respect to the first swash plate 18. Priority should be given to securing the thickness Y2 of the outer peripheral portion 51-2 in the above.
- the preferred force is that the thickness Y2 of the outer peripheral portion 51-2 in the second swash plate 51 is 1Z3 or more of the thickness X of the outer peripheral portion 18-1 in the first swash plate 18 and the outer peripheral portion 18-1 It is to be set thinner than the sheet thickness X of.
- the inventor of the present application has made the first swash plate 18 be made of iron, the second swash plate 51 to be made of bearing steel, and the second swash plate 51 to have the thickness Y2 of the outer peripheral portion 51-2 as the first swash plate.
- the configuration of 1Z3 of the thickness X of the outer peripheral portion 18-1 at 18 and thinner than the thickness X of the outer peripheral portion 18-1 under a high load (discharge capacity 100%) with a high discharge pressure, The test operation was performed for 100 hours.
- the thickness X of the outer peripheral portion 18-1 was in the range of 5-6 mm. In this test operation, no problem (for example, deformation of the second swash plate 51) occurred, and a result that could be put into practical use was obtained.
- the thickness Y1 of the inner peripheral portion 51-1 is larger than the thickness Y2 of the outer peripheral portion 51-2.
- the thick inner peripheral portion 51-1 stabilizes the support of the second swash plate 51 by the radial bearing 52 ⁇ / b> A, and can further improve the sliding between the first swash plate 18 and the second swash plate 51.
- the outer peripheral portion 51-2 of the second swash plate 51 which is relatively thinner than the inner peripheral portion 51-1, allows the outer peripheral portion 18- of the first swash plate 18 to be stronger in strength than the second swash plate 51. (1) It is easy to secure the plate thickness.
- the thickness Y2 of the outer peripheral portion 51-2 of the second swash plate 51 is smaller than the thickness X of the outer peripheral portion 18-1 of the first swash plate 18. Therefore, the thin outer peripheral portion 51-2 of the second swash plate 51 facilitates securing the thickness of the outer peripheral portion 18-1 of the first swash plate 18, which is stricter in strength than the second swash plate 51.
- the thickness Y1 of the inner peripheral portion 51-1 is larger than the thickness X of the outer peripheral portion 18-1 of the first swash plate 18. Therefore, the support of the second swash plate 51 by the radial bearing 52A is further stabilized.
- the outer diameter Z2 of the second protrusion 57 in the first protrusion 56 and the second protrusion 57 constituting the inner peripheral portion 51-1 of the second swash plate 51. Is smaller than the outer diameter Z1 of the first protrusion 56.
- the second protrusion 57 is, for example, in a state where the discharge capacity of the compressor 10 is the maximum (the state in FIG. 1). A part comes extremely close to the piston 23B at the bottom dead center position. Therefore, making the second projecting portion 57 smaller in diameter than the first projecting portion 56 and separating it from the piston 23 avoids the interference between the second swash plate 51 and the bistone 23 and reduces the second swash plate. This is effective in increasing the thickness Y1 of the inner peripheral portion 51-1 of the plate 51.
- an inclined surface is provided at the outer peripheral angle 57a of the tip end surface.
- a part of the outer peripheral angle 57a of the tip end surface is extremely close to the piston 23B at the bottom dead center position in a state where the discharge capacity of the compressor is maximum. Therefore, providing the inclined surface at the outer peripheral angle 57a of the distal end surface of the second protrusion 57 prevents interference between the second swash plate 51 and the piston 23 and reduces the inner peripheral portion of the second swash plate 51. This is effective in achieving a balance between increasing the thickness Y1 of 51-1.
- a portion of the outer peripheral edge of the first swash plate 18 corresponding to the piston 23A at the top dead center position has a slope at the convex corner 18c opposite to the second swash plate 51. Is provided. Therefore, the force S can be applied to the first swash plate 18 and the second swash plate 51 with a large diameter while suppressing a decrease in the durability and an increase in the size of the piston 23. Therefore, the contact slidability between the second swash plate 51 and the second shoe 25B is improved, and the durability of the second swash plate 51 and the second shoe 25B is suppressed while suppressing the reduction in the durability and the size of the piston 23. Performance can be improved.
- the first swash plate 18 inclined with respect to the drive shaft 16 has a convex corner portion 18c (inclined on the opposite side of the second swash plate 51) at the outer peripheral edge corresponding to the piston 23A at the top dead center position.
- the state without a surface protrudes largely in the radial direction of the drive shaft 16.
- the neck of the piston 23 corresponding to the protruding portion is formed in order to avoid interference with the protruding portion. It is conceivable to reduce the thickness of the 38 or increase the diameter of the neck 38 in the radial direction. However, reducing the thickness of the neck 38 leads to a decrease in the durability of the piston 23, and increasing the size of the neck 38 leads to an increase in the size of the compressor.
- Rollers 52g are used as rolling elements of the radial bearing 52A.
- a rolling bearing using a roller of 52 g as a rolling element is superior in load resistance compared to, for example, a case using a ball as a rolling element. This leads to downsizing of the radial bearing 52A and downsizing of the compressor 10.
- a race 55 is interposed between the roller 58a of the thrust bearing 58 and the first swash plate 18.
- the race 55 is rotatable relative to the first swash plate 18.
- a locking portion 18e protrudes from the outer peripheral portion 18-1 of the first swash plate 18 toward the second swash plate 51, and abuts the locking portion 18e. As a result, the race 55 is locked to the first swash plate 18 on the radially outer side.
- the race 55 is locked to the first swash plate 18 radially inward by providing a locking portion on the inner peripheral portion of the first swash plate 18.
- the lubricating oil refrigerant oil
- the race 55 is engaged with the first swash plate 18 on the radial outside
- the lubricating oil enters between the first swash plate 18 and the race 55 by the engagement portion 18e. It is possible to prevent the swash plate from being hindered and to make the sliding between the first swash plate 18 and the race 55 good.
- the locking portion 18e has an annular shape. Therefore, the race 55 The locking is performed stably, and the sliding between the race 55 and the first swash plate 18 is further improved.
- the second swash plate 51 is eccentrically arranged with respect to the first swash plate 18 toward the piston 23A at the top dead center position. That is, the second swash plate 51 is displaced toward the second shoe 25B of the piston 23 near the top dead center position. Therefore, without increasing the diameter of the first swash plate 18 and the second swash plate 51, the contact area between the second swash plate 25B of the piston 23 near the top dead center position (compression stroke) and the second swash plate 51 can be increased. it can.
- the inertial force in the swinging motion of the second swash plate 51 performing such a swinging motion affects the high-speed controllability similarly to the inertial force in the reciprocating motion of the piston 23.
- the weight reduction of the second swash plate 51 reduces the inertial force in the swing of the second swash plate 51, and reduces the influence of the inertial force in the swing motion of the second swash plate 51 on the high-speed controllability. Bring. In other words, if the weight of the second swash plate 51 is reduced, high-speed controllability is improved.
- the outer peripheral angle 57a of the second projection 57 is provided with a tapered inclined surface (chamfered).
- Such a chamfer structure results in a lightweight siding of the second swash plate 51.
- the support portion 39 is not eccentric with respect to the center axis Ml of the first swash plate 18. That is, the second swash plate 51, the radial bearing 52A, and the thrust bearing 58 (including the race 55) are not eccentric with respect to the first swash plate 18.
- the portion corresponding to the piston 23B at the bottom dead center position is such that the convex corner 18d on the second swash plate 51 side is radially larger than the second swash plate 51. Since it does not protrude greatly, as shown in FIG. 6, there is no problem even if an inclined surface (chamfer) is not provided at the convex corner portion 18d.
- the PCD force of the thrust bearing 58 is centered on the center axes Ml and M2 of the first swash plate 18 and the second swash plate 51, and the center point P of the first and second showers 25A and 25B. Is larger than the diameter of the virtual cylinder passing through. In this way, the thrust bearing 58 (the roller 58a) can suitably receive the compression reaction force transmitted via the second swash plate 51, and the durability is improved.
- the “PCD” of the thrust bearing 58 means the center of the thrust bearing 58 (the center axes Ml and M2 of the first swash plate 18 and the second swash plate 51) as the center axis, and the roller 58a has a center on the rotation center axis. Refers to the diameter of a virtual cylinder passing through a point.
- the second swash plate 51 has a plurality of lightening holes 59 formed therethrough in the thickness direction.
- the lightening holes 59 are provided at equal angular intervals around the center of the ring of the second swash plate 51.
- the plurality of lightening holes 59 are provided inside the arrangement region of the rollers 58a arranged in an annular shape in the thrust bearing 58, so that the rollers 58a and the lightening holes 59 do not interfere with each other.
- the plurality of lightening holes 59 contribute to weight reduction of the second swash plate 51.
- the configuration in which the plurality of lightening holes 59 are provided in the second swash plate 51 has the same effect as the item (3-13) in the third embodiment.
- annular lightening concave portion 60 is formed around the inner peripheral portion 51-1, and on the rear surface of the second swash plate 51, an annular lightening concave portion 61 is formed. Is formed around the inner peripheral portion 51-1.
- the lightening concave portions 60 and 61 are provided inside the arrangement region of the rollers 58a arranged in an annular shape in the thrust bearing 58, so that the rollers 58a and the lightening concave portions 60 do not interfere with each other.
- the lightening recesses 60 and 61 contribute to the lightweight siding of the second swash plate 51.
- the configuration in which the lightening concave portions 60 and 61 are provided in the second swash plate 51 has the same effect as the item (3-13) in the third embodiment.
- the PCD of the thrust bearing 58 is set at the center point P of the first shower 25A and the second shower 25B around the center axes Ml and M2 of the first swash plate 18 and the second swash plate 51. It is smaller than the diameter of the passing virtual cylinder C1. In this way, the thrust bearing 58 (the roller 58a) can suitably receive the compression reaction force transmitted through the second swash plate 51, and the durability is improved.
- the “PCD” of the thrust bearing 58 is defined as the center axis of the thrust bearing 58 (the center axes Ml and M2 of the first swash plate 18 and the second swash plate 51) and the rotation center axis of the roller 58a. Refers to the diameter of the virtual cylinder C2 passing through the midpoint on the line.
- the inventor of the present application sets the inclination angle of the swash plate (the first swash plate 18 and the second swash plate 51) [the inclination angle ⁇ (shown in FIG. 10) of the center axes Ml and M2 with respect to the axis L of the drive shaft 16].
- ⁇ shown in FIG. 10
- discharge pressure 13.5 MPa
- number of pistons 23 9, number of rollers 58a 36, length of rollers 58a 6.8 mm, diameter of rollers 58a 3 mm 100 hours of test operation It was.
- the inventors of the present application assume that the radius of the virtual cylinder C2 is 3.4 mm larger than the radius of the virtual cylinder C1 (the roller 58a has a length of 6.8 mm and the radial direction of the thrust bearing 58 is only 50%). And the radius of the virtual cylinder C2 is 4.08 mm larger than the radius of the virtual cylinder C1 (the roller 58a has a radius of the thrust bearing 58 by 60% of its length 6.8 mm).
- the test operation was performed for 100 hours under the above-mentioned conditions. If the radius of the virtual cylinder C2 is 3.4 mm larger than the radius of the virtual cylinder C1, no flaking occurs. If the radius of the virtual cylinder C2 is 4.08 mm larger than the radius of the virtual cylinder C1, the flaking occurs. King arose.
- rollers 58a be shifted from the inside to the outside or from the outside to the inside in the radial direction of the thrust bearing 58 by 50% of the length of the rollers 58a.
- the second swash plate 51 has an inner peripheral portion 51c at a position corresponding to the inner end of each oil groove 51d.
- a through hole 5 If penetrating in the thickness direction of the plate 51 is formed, and the oil groove 51 d is directly opened to the crank chamber 15 at one end thereof. By doing so, the amount of oil introduced from the crank chamber 15 into the oil groove 51d increases, and the sliding between the second swash plate 51 and the first swash plate 18 can be improved.
- a through hole 5 lg formed through the first swash plate 18 in the plate thickness direction serves as an oil introduction passage. It may be configured.
- the coating 54 made of a solid lubricant was formed on the front surface (the region 51b-1 and the region 51c-1) of the second swash plate 51.
- the coating 54 may be deleted, and the sintered metal may be sprayed on the front surface (region 51b-1 and region 51c-1) of the second swash plate 51.
- the front surface (region 51b-1 and region 51c-1) of the second swash plate 51 becomes a surface having minute irregularities due to the sintered metal, and the oil retaining force of the surface is improved, and The coefficient of friction at the sliding portion between the first swash plate 18 and the second swash plate 51 can be reduced.
- the bearing that rotatably supports the second swash plate 51 in the first swash plate 18 is not limited to the ball bearing 52 used in each of the above embodiments. Also, a slide bearing may be used.
- the present invention is applied to a compressor having a double-ended piston.
- the present invention is not limited to application to a refrigerant compressor used in a refrigeration circuit, but may be applied to, for example, an air compressor.
- the third embodiment is changed, for example, as shown in FIG. 6, the sliding contact surface 25b of the first shoe 25A is made flat.
- the sliding contact surface 25b of the second shoe 25B is formed to have a concave shape with a concave central portion.
- the weight of the second shoe 25B reciprocating linearly with the piston 23 can be reduced, the inertia force of the second shoe 25B can be reduced, and the first swash plate 18 and the second swash plate 51 can be reduced.
- the change of the inclination angle that is, the change of the displacement of the compressor, can be performed smoothly.
- the radial bearing 52A is changed to a rolling bearing having balls as rolling elements.
- the radial bearing 52A is changed to a plain bearing.
- the thrust bearing 58 is changed to a rolling bearing having a ball as a rolling element.
- the thrust bearing 58 is changed to a slide bearing.
- the radial bearing 52A is configured to receive only the radial load (load in the direction orthogonal to the center axis M2) acting on the second swash plate 51.
- the radial bearing 52A can be used not only for the radial load but also for the thrust load (in the direction along the center axis M2). Load).
- the thrust bearing 58 is configured to receive only the thrust load acting on the second swash plate 51.
- the rollers 58a By changing this, for example, by arranging the rollers 58a so as to be inclined with respect to the board surface of the second swash plate 51, a structure capable of receiving not only a thrust load but also a radial load is adopted.
- the thickness Y1 of the inner peripheral portion 51-1 of the second swash plate 51 is larger than the thickness X of the outer peripheral portion 18-1 of the first swash plate 18. .
- the thickness Y1 of the inner peripheral portion 51-1 of the second swash plate 51 should be equal to or smaller than the thickness X of the outer peripheral portion 18-1 of the first swash plate 18. .
- the thickness Y1 of the inner peripheral portion 51-1 is larger than the thickness Y2 of the outer peripheral portion 51-2. This shall be changed so that the thickness Y1 of the inner peripheral portion 51-1 and the thickness Y2 of the outer peripheral portion 51-2 are the same. By doing so, the shape of the second swash plate 51 is simplified, and the manufacture of the second swash plate 51 is facilitated.
- the first projecting portion 56 and the second projecting portion 57 that constitute the inner peripheral portion 51-1 of the second swash plate 51 are the same as the second projecting portion 57.
- the outer diameter Z2 of the first protruding portion 56 is smaller than the outer diameter Z1 of the first protruding portion 56, and the second protruding portion 57 is provided with a slope at the outer peripheral angle 57a of the distal end surface.
- the outer diameter Z2 of the second projecting portion 57 is made smaller than the outer diameter Z1 of the first projecting portion 56, and the outer peripheral angle 57a of the distal end surface of the second projecting portion 57 is tapered. of Either one of the inclined surfaces (chamfered) shall be provided.
- the inner peripheral portion 51-1 of the second swash plate 51 is provided with the first projecting portion 56 and the second projecting portion 57, so that the outer peripheral portion 51-1 is provided.
- the thickness was larger than 2.
- the inner peripheral portion 51-1 of the second swash plate 51 is provided with only one of the first protruding portion 56 and the second protruding portion 57, so that the outer peripheral portion 51-2 is provided. Also, make the board thicker.
- the locking portion 18e is omitted, and a locking portion is provided on the inner peripheral portion of the first swash plate 18 (for example, the locking portion is provided at the base of the support portion 39). In other words, the race 55 is locked to the first swash plate 18 on the radially inner side.
- the second swash plate 51 has a center axis M2 corresponding to the piston 23A at the top dead center position with respect to the center axis Ml of the first swash plate 18.
- the first and second shots 25 were shifted in parallel to the center point P side of 25A and 25B. That is, the center axis M2 of the second swash plate 51 is the center axis Ml of the first swash plate 18 and the center point P of the first and second shoes 25A and 25B corresponding to the piston 23A at the top dead center position. Existed on the determined plane.
- the center axis M2 of the second swash plate 51 is the center axis Ml of the first swash plate 18 and the center point P of the first and second shoes 25A and 25B corresponding to the piston 23A at the top dead center position. It suffices that the plane is shifted from the plane orthogonal to the determined plane by the center axis Ml toward the piston 23A at the top dead center.
- the first shoe 25A corresponding to the piston 23A at the top dead center position is required.
- the center point P of A and the second show 25B is at a position of 0 ° around the center axis Ml
- the second swash plate 51 is moved so that the center axis M2 passes through a point within a range of 45 ° on the soil. It is good to be eccentric with respect to the plate 18.
- a support for rotatably supporting the second swash plate via the bearing is provided on the first swash plate.
- the second swash plate is disposed in a state where the support portion is inserted through a support hole formed through the center of the second swash plate, and the bearing is provided with an outer ring.
- the first swash plate is provided with a locking portion protruding toward the second swash plate, and the race is radially moved by the contact with the locking portion.
- the swash plate compressor according to claim 9 wherein the swash plate compressor is locked to the swash plate.
- the first and second shoes each have a hemispherical shape, and the centers of curvature of the first and second shoes are coincident, and the center of curvature is located on the center axis of the piston.
- the PCD of the thrust bearing is larger than the diameter of an imaginary cylinder passing through the center point of curvature of the first and second shows with the center axis of the first swash plate as the center axis.
- the first and second shoes each have a hemispherical shape, and the centers of curvature of the first and second shoes coincide with each other.
- the center of curvature is located on the center axis of the piston.
- the PCD of the thrust bearing is smaller than the diameter of an imaginary cylinder passing through the center of curvature of the first and second showers with the center axis of the first swash plate as the center axis.
- a first swash plate is connected to the drive shaft so as to be integrally rotatable, a second swash plate is supported by the first swash plate, and the first and second swash plates are A piston is moored via a first shoe abutting on the first swash plate and a second shoe on a side receiving a compression reaction force abutting on the second swash plate, and the second shaft accompanying the rotation of the drive shaft.
- the second swash plate is rotatable relative to the first swash plate via a bearing.
- a swash plate compressor characterized by being supported.
- the bearing here is at least one of a thrust bearing and a radial bearing.
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP04771373A EP1669601A1 (en) | 2003-09-02 | 2004-08-06 | Swash plate compressor |
US10/570,470 US7455008B2 (en) | 2003-09-02 | 2004-08-06 | Swash plate compressor |
JP2005513611A JPWO2005024234A1 (ja) | 2003-09-02 | 2004-08-06 | 斜板式圧縮機 |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2003310290 | 2003-09-02 | ||
JP2003-310290 | 2003-09-02 | ||
JP2003326962 | 2003-09-18 | ||
JP2003-326962 | 2003-09-18 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005024234A1 true WO2005024234A1 (ja) | 2005-03-17 |
Family
ID=34277687
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2004/011374 WO2005024234A1 (ja) | 2003-09-02 | 2004-08-06 | 斜板式圧縮機 |
Country Status (5)
Country | Link |
---|---|
US (1) | US7455008B2 (ja) |
EP (1) | EP1669601A1 (ja) |
JP (1) | JPWO2005024234A1 (ja) |
KR (1) | KR100679909B1 (ja) |
WO (1) | WO2005024234A1 (ja) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4483699B2 (ja) * | 2005-01-27 | 2010-06-16 | 株式会社豊田自動織機 | 斜板式圧縮機 |
JP2006291881A (ja) * | 2005-04-13 | 2006-10-26 | Toyota Industries Corp | 斜板式圧縮機 |
JP5495622B2 (ja) * | 2009-05-28 | 2014-05-21 | 大豊工業株式会社 | シュー |
CN109863301A (zh) | 2016-07-25 | 2019-06-07 | 开罗股份有限公司 | 摇摆板式压缩机和使用它的氧气浓缩器 |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH05195950A (ja) * | 1992-01-23 | 1993-08-06 | Nippondenso Co Ltd | 斜板型圧縮機 |
JPH0828447A (ja) * | 1994-05-13 | 1996-01-30 | Toyota Autom Loom Works Ltd | ピストン式圧縮機における動力低減構造 |
JPH08338363A (ja) * | 1995-06-08 | 1996-12-24 | Toyota Autom Loom Works Ltd | 斜板式圧縮機 |
JPH09105376A (ja) * | 1995-10-11 | 1997-04-22 | Zexel Corp | 可変容量型斜板式圧縮機 |
JPH10196525A (ja) * | 1997-01-09 | 1998-07-31 | Sanden Corp | 斜板式圧縮機 |
JP2001032768A (ja) * | 1999-07-19 | 2001-02-06 | Zexel Valeo Climate Control Corp | 可変容量型斜板式圧縮機 |
JP2002180955A (ja) * | 2001-10-22 | 2002-06-26 | Toyota Industries Corp | 容量可変型斜板式圧縮機 |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH03141877A (ja) | 1989-10-25 | 1991-06-17 | Hitachi Ltd | 斜板式圧縮機 |
-
2004
- 2004-08-06 EP EP04771373A patent/EP1669601A1/en not_active Withdrawn
- 2004-08-06 KR KR1020067004238A patent/KR100679909B1/ko not_active IP Right Cessation
- 2004-08-06 US US10/570,470 patent/US7455008B2/en not_active Expired - Fee Related
- 2004-08-06 WO PCT/JP2004/011374 patent/WO2005024234A1/ja active IP Right Grant
- 2004-08-06 JP JP2005513611A patent/JPWO2005024234A1/ja active Pending
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH05195950A (ja) * | 1992-01-23 | 1993-08-06 | Nippondenso Co Ltd | 斜板型圧縮機 |
JPH0828447A (ja) * | 1994-05-13 | 1996-01-30 | Toyota Autom Loom Works Ltd | ピストン式圧縮機における動力低減構造 |
JPH08338363A (ja) * | 1995-06-08 | 1996-12-24 | Toyota Autom Loom Works Ltd | 斜板式圧縮機 |
JPH09105376A (ja) * | 1995-10-11 | 1997-04-22 | Zexel Corp | 可変容量型斜板式圧縮機 |
JPH10196525A (ja) * | 1997-01-09 | 1998-07-31 | Sanden Corp | 斜板式圧縮機 |
JP2001032768A (ja) * | 1999-07-19 | 2001-02-06 | Zexel Valeo Climate Control Corp | 可変容量型斜板式圧縮機 |
JP2002180955A (ja) * | 2001-10-22 | 2002-06-26 | Toyota Industries Corp | 容量可変型斜板式圧縮機 |
Also Published As
Publication number | Publication date |
---|---|
JPWO2005024234A1 (ja) | 2006-11-02 |
US20070039459A1 (en) | 2007-02-22 |
EP1669601A1 (en) | 2006-06-14 |
US7455008B2 (en) | 2008-11-25 |
KR20060057625A (ko) | 2006-05-26 |
KR100679909B1 (ko) | 2007-02-07 |
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