WO2004015269A1 - 容量可変型圧縮機 - Google Patents
容量可変型圧縮機 Download PDFInfo
- Publication number
- WO2004015269A1 WO2004015269A1 PCT/JP2003/010094 JP0310094W WO2004015269A1 WO 2004015269 A1 WO2004015269 A1 WO 2004015269A1 JP 0310094 W JP0310094 W JP 0310094W WO 2004015269 A1 WO2004015269 A1 WO 2004015269A1
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- WO
- WIPO (PCT)
- Prior art keywords
- rotor
- swash plate
- plane
- variable displacement
- displacement compressor
- Prior art date
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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
- F04B27/1072—Pivot mechanisms
Definitions
- the present invention relates to a variable displacement compressor incorporated in a refrigeration circuit of a vehicle air conditioner, for example.
- variable displacement compressor there is, for example, one disclosed in Japanese Patent Application Laid-Open No. 2001-304102. That is, the pistons are housed in the plurality of cylinder bores formed in the housing, respectively.
- a rotor is rotatably provided on the drive wheel rotatably supported by the housing.
- a cam plate (swash plate) is supported on the drive shaft so that it can slide and tilt.
- a hinge mechanism is provided between the rotor and the cam plate. Rotational motion of the drive shaft is converted to reciprocating motion of biston via the rotor, hinge mechanism and cam plate to compress the refrigerant gas.
- the hinge mechanism guides the cam plate so that the cam plate slides while tilting on the drive shaft.
- the stroke of the piston that is, the displacement of the variable displacement compressor is changed according to the inclination angle of the cam plate.
- the hinge mechanism includes two arms extending from the cam plate toward the rotor, and a protrusion extending from the rotor toward the cam plate and inserted between opposing wall surfaces of the two arms. .
- the projection has a pair of side surfaces facing the opposing wall surfaces of both arms, respectively. Power is transmitted between the rotor and the cam plate in a state where the projection is in surface contact with and pressed against one wall surface of both arms. Therefore, when the cam plate is tilted, one arm is slid with respect to the projection while maintaining a state in which the wall surface of one arm and one side surface of the projection are in surface contact.
- the arm in order to smoothly change the discharge capacity of the variable displacement compressor, that is, to achieve a smooth tilting of the cam plate, the arm is kept in surface contact with the projection and the upper surface of the variable displacement compressor is kept in contact with the projection. It is desirable to slide. In other words, if the cam plate force is inclined so that the protrusion is twisted between the two arms due to the biasing effect of the axial load caused by the compression reaction force, the sliding resistance between the arm and the protrusion increases. I will. Therefore, problems such as early wear of the arm and the projection, that is, deterioration of the durability of the hinge mechanism, and deterioration of the discharge capacity controllability of the variable displacement compressor due to the inability of the hinge mechanism to operate smoothly occur.
- An object of the present invention is to provide a variable displacement compressor capable of realizing a smooth discharge capacity change while suppressing processing costs.
- a piston is housed in a cylinder bore in a housing, a rotor is rotatably provided on a drive shaft rotatably supported by the housing, and the drive shaft is A cam plate is supported so as to be slidable and tiltable, a hinge mechanism is provided between the rotor and the cam plate, and the rotational movement of the drive shaft is controlled by the rotor, the hinge mechanism and the hinge mechanism.
- the reciprocating motion of the biston is converted via a cam plate, and the cam plate slides while tilting on the drive shaft by the hinge mechanism.
- a variable displacement compressor capable of changing the output capacity
- the hinge mechanism is a first member that is one of the rotor and the force plate and the other of the port and the force plate.
- a first hinge portion extending toward the second member, and a second hinge portion extending from the second member toward the first member.
- One of them is at least two wall portions, the other is a projection inserted between the two wall portions, the both wall portions have opposing surfaces facing each other, and the projection is the both wall portions.
- a pair of opposing surfaces that respectively face the opposing surfaces, and one of the protruding surfaces is in planar contact with the opposing surface of one of the walls, whereby the rotor and the cam plate are brought into contact. Power transmission between at least one of the opposing surfaces.
- Another is to provide a variable displacement compressor provided with a lightening portion.
- FIG. 1 is a longitudinal sectional view of a variable displacement compressor according to a first embodiment of the present invention.
- FIG. 2 is a plan view showing a rotor provided in the compressor of FIG.
- FIG. 3 is a plan view showing a swash plate provided in the compressor of FIG.
- FIG. 4 is a partially enlarged cross-sectional view showing an engagement state between the rotor of FIG. 2 and the swash plate of FIG.
- FIG. 5 is a partially enlarged cross-sectional view showing a tip end of a swash plate protrusion in the second embodiment of the present invention.
- FIG. 6 is a partially enlarged longitudinal sectional view showing a variable displacement compressor including a ring member according to a third embodiment of the present invention.
- FIG. 7 is a partially enlarged cross-sectional view showing a contact state between the ring member and the swash plate shown in FIG. 6, as viewed from above in FIG.
- FIG. 8 is a plan view showing a rotor and a swash plate according to a fourth embodiment of the present invention.
- FIG. 9 is a side view of the rotor and the swash plate shown in FIG. BEST MODE FOR CARRYING OUT THE INVENTION
- Figure 1 shows a longitudinal section of a variable displacement compressor (hereinafter simply referred to as a compressor).
- the compressor housing (compressor housing) is composed of a cylinder block 11, a front housing 12 fixedly joined to the front end of the cylinder block 11, and a cylinder block 11 At the rear end, there is provided a lya housing 14 fixedly connected via a valve / port forming body (valve assembly) 13.
- a crank chamber 15 is formed between the cylinder block 11 and the front housing 12.
- a drive shaft 16 is rotatably supported by the cylinder block 11 and the port housing 12 so as to pass through the crank chamber 15.
- the drive shaft 16 is equipped with an engine E,
- a substantially disk-shaped rotor 17 is fixed to the drive shaft 16 so as to be rotatable.
- a substantially disk-shaped swash plate 18 as a cam plate is accommodated in the crank chamber 15 ⁇ .
- One of the rotor 17 and the swash plate 18 corresponds to a first member, and the other of the rotor 17 and the swash plate 18 corresponds to a second member.
- the c insertion hole 2 0 ⁇ hole 2 0 is formed through being driven shaft 1 6 ⁇ , the swash plate 1 8 slide on the drive shaft 1 6 D • It is supported so that it can tilt and tilt.
- a hinge mechanism 19 is provided between the rotor 17 and the swash plate 18. The hinge mechanism 19 rotates the swash plate 18 synchronously with the rotor 17 and the drive shaft 16, and the swash plate 18 slides on the drive shaft 16 along the axis L of the drive shaft 16. To allow.
- a plurality of cylinder pores 22 are formed at equal angular intervals around the axis L of the drive shaft 16 in the cylinder block 11. Cylinder bore 2 2 is drive shaft 1
- the single-headed piston 23 is reciprocally accommodated in each cylinder bore 22.
- the front and rear openings of the cylinder bore 22 are respectively closed by the front end face 13 a of the valve port forming body 13 and the corresponding bistone 23, and the corresponding piston 23 is provided in the cylinder bore 22.
- a compression chamber 24 whose volume changes according to the reciprocating motion is defined.
- Each piston 23 is moored to the outer periphery of the swash plate 18 via a pair of hemispherical shoes 25. Therefore, the drive shaft
- a suction chamber 26 and a discharge chamber 27 are respectively formed between the valve port forming body 13 and the rear housing 14.
- the valve / port forming body 13 has a suction port 28, a suction valve 29, a discharge port 30, and a discharge valve 31 corresponding to the cylinder bore 22.
- the refrigerant gas in the suction chamber 26 flows into the compression chamber 24 via the suction port 28 and the suction valve 29 as each piston 23 moves from the top dead center position to the bottom dead center position. Inhaled.
- the refrigerant gas sucked into the compression chamber 24 is compressed to a predetermined pressure as the piston 23 moves from the bottom dead center position to the top dead center position, and is discharged to the discharge port 30.
- the gas is discharged to the discharge chamber 27 through the discharge valve 31.
- a bleed passage 32, an air supply passage 33, and a control valve 34 are provided in the compressor housing.
- the bleed passage 3 2 is connected to the crank chamber 15 and the suction chamber. 2 Connect to 6.
- the air supply passage 33 connects the discharge chamber 27 to the crank chamber 15.
- the control valve 34 composed of an electromagnetic valve is disposed in the middle of the air supply passage 33.
- 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 swash plate 18 is changed accordingly.
- the stroke of the tonnes 23 or the discharge of the compressor is adjusted.
- the inclination angle of the swash plate 18 is represented by an angle with respect to a plane orthogonal to the axis L of the drive shaft 16. For example, when the opening degree of the control valve 34 decreases, the internal pressure of the crank chamber 15 decreases. Then, the inclination angle of the swash plate 18 increases, the stroke of the piston 23 increases, and the discharge capacity of the compressor increases.
- the maximum inclination angle of the swash plate 18 is defined by a protrusion (maximum inclination angle defining portion) 18 a protruding from the front surface of the swash plate 18 abutting on the rear surface of the rotor 17.
- a protrusion maximum inclination angle defining portion
- the minimum tilt angle of the swash plate 18 is defined by a minimum tilt angle defining section 35 provided on the drive shaft 16.
- the minimum inclination angle defining portion 35 includes a coil spring 35a wound around the drive shaft 16 and a circlip (snap) fixed to the drive shaft 16 and functioning as a panel seat for the coil spring 35a. Ring) consists of 3 5b.
- the coil spring 35a urges the center of the rear surface of the swash plate 18 toward the front of the compressor, that is, in the direction in which the inclination angle of the swash plate 18 increases.
- a coil spring 36 is wound around the drive shaft 16 between the rear surface of the rotor 17 and the front surface of the swash plate 18.
- the coil spring 36 urges the center of the front surface of the swash plate 18 toward the rear of the compressor, that is, in the direction in which the inclination angle of the swash plate 18 decreases.
- the biasing force of the coil spring 36 and the biasing force of the coil spring 35 a of the defining portion 35 contribute to the determination of the tilt angle of the swash plate 18.
- the swash plate 18 has a top dead center corresponding portion TDC for disposing the piston 23 at the top dead center position.
- the top dead center corresponding portion TDC includes the center point of the spherical surface of both shoes 25 corresponding to biston 23 at the top dead center position.
- an engagement groove 41 is formed on the rear surface of the rotor 17 at a position facing the top dead center corresponding portion TDC of the swash plate 18.
- the engagement groove 41 is formed by two rotor-side projections 42 and 43 extending from the rear surface of the rotor 17 toward the swash plate 18.
- the two rotor-side projections 42, 43 are provided at front and rear positions in the rotation direction of the rotor 17 (the direction indicated by the arrow R in FIG. 2 or the reverse direction).
- the two rotor-side projections 42 and 43 function as two walls extending from the rotor 17 to the swash plate 18 to form the engagement groove 41.
- the rotor side projections 42, 43 have side surfaces (opposing surfaces) 42a, 43a facing each other in the engagement groove 41.
- a protrusion 44 extending toward the rotor 17 is provided on a portion of the front surface of the swash plate 18 facing the engagement groove 41.
- the protrusion 44 includes two swash plate-side protrusions 45 and 46.
- Both swash plate side projections 45 and 46 are symmetrical in the rotational direction of the drive shaft 16 (the direction indicated by the arrow R in FIG. 3 or the reverse direction) in the rotational direction across the top dead center corresponding portion TDC. Is located in the position.
- the projecting portion 44 has a hollow structure in which two swash plate side projections 45 and 46 are left on both sides to reduce the weight of the swash plate 18.
- one of the rotor-side protrusions 42, 43 and the protrusion 44 corresponds to a first hinge portion, and the rotor-side protrusions 42, 43, and the protrusion The other of them corresponds to the second hinge part.
- the two swash plate side projections 45 and 46 are respectively inserted into the engagement grooves 41 from the front ends thereof.
- the two swash plate side projections 45 and 46 have side surfaces 45a and 46a facing each other, and the side surfaces (opposing surfaces) 45a and 45b are rotor-side projections facing the same.
- the side surfaces 42a and 43a of the surfaces 42 and 43 can be abutted in a plane.
- the swash plate 18 is transmitted to the swash plate 18 via the side surface 45 a of the plate-side protrusion 45. Conversely, when the drive shaft 16 rotates in the direction opposite to the direction of the arrow R, the rotational force of the rotor 17 is applied to the side surfaces 4 3a and 4 3a of the rotor side projections 43 serving as the power transmission side. The swash plate 18 is transmitted to the swash plate 18 via the side surface 46 a of the swash plate side projection 46 that comes into contact with the swash plate 18.
- the compressor according to the present embodiment has a structure in which the rotation direction of the engine of the vehicle on which the compressor is mounted is in any direction, in other words, the drive shaft 16 required by the user. It is configured to be able to suitably cope with any of the rotation directions of the arrow R and the direction opposite to the arrow R. Therefore, for example, the hinge mechanism 19 is configured to have a symmetrical shape in the rotational direction of the drive shaft 16 across the top dead center corresponding portion TDC in the rotational direction. In the engagement groove 41, a cam portion 47 as an axial load receiving portion is bulged at the base of each rotor-side projection 42, 43.
- a force surface 47a is formed on the rear end surface facing the swash plate 18 as the position approaches the axis L of the drive shaft 16 to the rear.
- cylindrical surfaces 45 b, 46 b force S which are convex curved surfaces are formed, respectively.
- the central axis S of each cylindrical surface 45b, 46b is the side surface 45a,
- each swash plate side projection 45, 46 is a cylindrical surface 4
- the tips of the swash plate side projections 45 and 46 are moved in a direction away from the drive shaft 16 on the cam surface 47a of the cam portion 47, so that the hinge mechanism 19 is tilted. Guide the increase in the angle of inclination of the plate 18. Conversely, when the compressor reduces the displacement, the swash plate 18 has a cylindrical surface 4 5 b, 4
- the inclination angle of the swash plate 18 can be changed by changing the side surface 42 a of the rotor-side projection 42 responsible for power transmission and the swash-plate side projection 45. Pressing sliding with the side surface 45a will be involved.
- the inclination angle of the swash plate 18 can be changed by changing the side surface 4 3 a of the rotor-side projection 43 that carries power transmission and the swash plate. Pressing sliding with the side surface 46 a of the side protrusion 46 will be involved.
- the cam surface 47a of the cam portion 47 and the cylindrical surfaces 45b, 46b of the swash plate side projections 45, 46 have improved durability against press contact sliding with each other. Quenching is performed for this purpose.
- the quenching is performed by, for example, induction hardening.
- the regions where the quenching process is performed in the hinge mechanism 19 are regions 50 and 51 indicated by dots in FIGS. 1 to 3, respectively. In other words, the quenching process is limited to a part of the hinge mechanism 19 including the cam surface 47 a of the cam portion 47 and the cylindrical surfaces 45 b and 46 b of the swash plate side projections 45 and 46. Has been given.
- the cylindrical surfaces 45b and 46b are each covered with a solid lubricant film.
- the solid lubricant include a fluororesin such as polytetrafluoroethylene and molybdenum disulfide.
- the swash plate 18 is inclined in a direction different from that when the discharge capacity is changed, by prying the projection 44 in the engagement groove 41 due to the biasing action of the axial load caused by the compression reaction force. Try to be inclined. More specifically, as shown in FIG. 3, assuming that the rotation direction of the drive shaft 16 is in the direction of arrow R, the swash plate 18 has a half-circumference portion on the compression stroke side, that is, the top dead center corresponding portions TDC and TDC. The left half of FIG. 3 around the virtual plane H including the axis L of the drive shaft 16 is a reaction force to be pushed forward from the piston 23 by the compression of the refrigerant gas. Receive.
- the swash plate 18 has a half-circumferential part on the suction stroke side, that is, a half-circumferential part on the right side in FIG. 3 with respect to the plane H being pulled backward from the piston 23 due to refrigerant gas suction. Receive the reaction force to be stretched. Accordingly, the swash plate 18 has the side surfaces 45a, 46a of the swash plate side protrusions 45, 46 with respect to the side surfaces 42a, 43a of the rotor side protrusions 42, 43 opposed to the side surfaces 45a, 46a. In this case, the nozzle is inclined in the clockwise direction in FIG. 3, that is, in a direction different from the direction when the discharge capacity is changed.
- the swash plate 18 is prevented from being inclined in a direction different from that when the discharge capacity is changed, in other words, the protrusion 44 is prevented from being twisted in the engagement groove 41.
- the play of the protrusion 44 is based on the distance X (see FIG. 2) between the mutually parallel side surfaces 42 a and 43 a of the two rotor-side protrusions 42 and 43.
- 46 are determined by the clearance, which is the value obtained by subtracting the distance Y (see Fig. 3) between the parallel sides 45a, 46a of the, 46.
- the clearance (X ⁇ Y) is set in a suitable range of 0.01 to 0.2 Oam, and more preferably in a range of 0.03 to 0.11 mm. That is, if the clearance (X ⁇ Y) is too small, the hinge mechanism 19 tends to be in a difficult state due to dimensional tolerances and thermal expansion of the rotor 17 and the swash plate 18. Also, if the clearance (X-Y) is too large, there is a problem that the protrusion 44 is twisted in the engagement groove 41. Therefore, the setting range of the clearance (X—Y) described above is determined by preventing the projection 44 from being twisted in the engagement groove 41 and by setting the hinge mechanism 19 due to the clearance (X—Y) being too small.
- the side surfaces 42a, 43a of the rotor-side projections 42, 43 are provided with recesses 61 as hollow portions. , 62 are formed.
- the side surfaces 42a, 43a of the rotor side protrusions 42, 43 come into planar contact with the side surfaces 45a, 46a of the opposing swash plate side protrusions 45, 46. It consists of a possible area (sliding surface 4 2a-1, 4 3a-1) and a non-sliding surface 4 2a-2, 4 3a-2 located in the recesses 6 1, 6 2. I have.
- the side surfaces 42a, 43a of the rotor-side projections 42, 43 are formed with the concave portions 61, 62 so that the side surfaces 42a, 43a can be slid compared to, for example, the case without the concave portions 61, 62.
- the area of the moving surfaces 4 2 a-1 and 4 3 a-1 is small.
- the recesses 6 1, 62 in the engagement groove 41 are provided adjacent to the cam portion 47 at the bases of the corresponding rotor side projections 42, 43.
- the ⁇ portions 6 1 and 6 2 slide along the extending direction of the cam surface 47 a, that is, the tip of the swash plate side projections 45 and 46 on the cam surface 47 a when the discharge capacity is changed.
- the groove extends along the trajectory.
- the non-sliding surfaces 42a-2,43a-2 in the turning portions 61,62 are continuous with the cam surface 47a of the cam portion 47. Therefore, the side surfaces 42a, 43a of the rotor-side projections 42, 43 and the side surfaces 42a, 43a (specifically, the sliding surfaces 42a-1, 43a-1) are perpendicular to the side surfaces 42a, 43a.
- the connecting portions (recessed corners 61 a, 62 a) of the cam portion 47 with the cam surface 47 a are arranged at positions where they enter the recesses 61, 62. That is, as shown in FIG.
- the concave corners 6 1 a, 6 2 serving as connecting portions between the side surfaces 42 a, 43 a of the rotor side protrusions 42, 43 and the cam surface 47 a of the cam portion 47. a is released from the tips of the swash plate side projections 45, 46 by forming the recesses 61, 62 with respect to the side surfaces 42a, 43a.
- the concave corners 6 1 a and 6 2 a in the concaves 6 1 and 62 are used to reinforce the rotor-side projections 4 2 and 43, that is, to relieve stress concentration on the concave corners 6 1 a and 62 a. For this purpose, it is formed in a concave curved shape.
- the present embodiment having the above configuration has the following operations and effects.
- the side surfaces 4 5 a of the swash plate side projections 45 and 46 are formed.
- the area of the sliding area (sliding surface 4 2 a-1, 4 3 a-1) with respect to 46 a has been significantly reduced compared to the case without the recesses 6 1 and 6 2 . Therefore, the finishing process for the side surfaces 42a and 43a of the rotor side projections 42 and 43 can be performed in a narrow range (sliding surfaces 42a-1 and 43a-1) and the finishing cost can be reduced. Can be reduced. Therefore, it is possible to reduce the manufacturing cost of the compressor while achieving a high-precision setting of the clearance of the projection 44 between the two rotor-side projections 42 and 43.
- the swash plate side projections which are caused by this riding, are against the concave corners 6 la, 62 a in the recesses 61, 62 or the side surfaces 42 a, 43 a of the rotor side projections 42, 43.
- the angular contact of the convex corners 45c and 46c of 45 and 46 can be prevented. Therefore, it is possible to prevent the generation of abnormal noise caused by the swash plate 18 performing the tilting for changing the discharge capacity in the state where the angular hit occurs.
- there are other advantages such as prevention of wear deterioration of the hinge mechanism 19 and smooth tilting of the swash plate 18 for changing the discharge capacity.
- the smooth displacement of the swash plate 18 makes it possible to quickly change the displacement of the compressor, so that, for example, the displacement can be increased quickly from a low displacement and the air conditioning feeling can be improved. Be improved. Also, since the convex corners 45c, 46c of the swash plate side projections 45, 46 do not run on the concave corners 61a, 62a, the convex corners 45c, 4c are not required. The chamfer at 6c can be minimized. Therefore, the swash plate side projections 45, 46 can be formed without increasing the width (width in the left-right direction in FIG. 3) of the cylindrical surfaces 45b, 46b of the swash plate side projections 45, 46. Can be widened. Therefore, the load resistance of the cylindrical surfaces 45b and 46b can be improved without increasing the weight of the swash plate 18.
- the concave portions 6 1 and 6 2 have a groove shape extending along the cam surface 47 a of the cam portion 47. That is, irrespective of the inclination angle 'of the swash plate 18 (the discharge capacity of the compressor), the side surfaces 4 2a and 4 3a of the rotor side projections 42 and 43 and the cam surface of the cam portion 47 are provided.
- the connection portion with the 47 a (recessed corner portion '6 la, 62 a) is surely released from the tip of the swash plate side projection 45, 46.
- the recess 6 1 , 62 can prevent the swash plate side projections 45, 46 from being raised with respect to the concave corners 61a, 62a.
- the cam surface 47 of the cam portion 47 On the side surfaces 4 2a and 4 3a of the rotor side projections 42 and 43, the area located on the base side of the rotor side projections 42 and 43 is the cam surface 47 of the cam portion 47. Since it is close to a, the cam surface 47a hinders access to tools and the like.
- HO sections 61 and 62 which do not require finishing of the inner surface, are provided in the areas located on the base side of the rotor side projections 42 and 43 on the side faces 42a and 43a. It has been done. Therefore, for example, the concave portions 6 1, 62 are formed on the rotor side on the side surfaces 42 a, 43 a.
- the concave portion 61 is provided on the side surface 42 a of the rotor side protrusion 42 serving as the power transmission side.
- the concave portion 62 is provided on the side surface 43a of the rotor-side projection 43 serving as the power transmission side.
- the side surfaces 42a, 43a of the rotor side projections 42, 43 on the power transmission side are surfaces on which the transmission torque between the rotor 17 and the swash plate 18 acts.
- Recesses 6 1, 6 2 are provided on both rotor side projections 42, 43. Therefore, when the rotation direction of the drive shaft 16 is in the direction of the arrow R, the concave portion 62 is also provided on the side surface 43a of the rotor-side projection 43 that is not on the power transmission side. Conversely, when the rotation direction of the drive shaft 16 is opposite to the direction of the arrow R, the concave portion 61 is also provided on the side surface 42 a of the rotor side protrusion 42 not on the power transmission side. That is, the effect of the above (5) is obtained regardless of whether the rotation direction of the drive shaft 16 is the direction of the arrow R or the direction opposite to the arrow R.
- the hinge mechanism 19 is hardened only in a part including a contact point between the rotor 17 and the swash plate 18 in the hinge mechanism 19. Therefore, compared to the case where the entire hinge mechanism 19 is quenched, for example, the occurrence of distortion, cracks, and the like due to quenching in the hinge mechanism 19 is suppressed. Therefore, for example, the accuracy of the clearance (X— ⁇ ) of the protrusion 44 between the rotor-side protrusions 42 and 43, such as the hinge, The amount of finishing work required to maintain the dimensional accuracy of the mechanism 19 is reduced, and costs can be reduced.
- FIG. 5 shows a second embodiment.
- the side walls 42a, 43a of the rotor-side projections 42, 43 are provided with lightening portions (recesses 61, 62).
- the lightening portions are deleted from the side surfaces 42 a, 43 a of the rotor side protrusions 42, 43, and the swash plate side protrusions 45 are formed.
- 46 are provided with lightening portions on the side surfaces 45a, 46a.
- the connecting portions recessed portions 61a, 62 of the side surfaces 42a, 43a of the rotor-side protrusions 42, 43 and the cam surface 47a of the cam portion 47 are formed.
- the convex corners 45c, 46c of the swash plate side projections 45, 46 Is chamfered more than in the first embodiment.
- the lightening portions provided on the side surfaces 45a and 46a of the swash plate side projections 45 and 46 will be described.
- the lightening portion provided on the side surface 46a of the other swash plate side projection 46 is the same as the lightening portion provided on the side surface 45a of the other swash plate side projection 45. The description is omitted.
- the side surface 42 a of the rotor side projection 42 (sliding surface 42 a-1) ) Is connected to the area (first plane 45 a-1) that mainly slides with respect to the first plane 45 a-1.
- a second flat surface 45 a-2 is formed.
- the second plane 45a-2 is formed by machining after the swash plate 18 is formed, that is, after the chamfering of the convex corner 45c.
- the central axis S of the cylindrical surface 45b is perpendicular to the first virtual plane 1 including the first plane 45a-1.
- the second plane 45 a-2 is inclined so that the tip end side of the swash plate side projection 45 is separated from the side surface 42 a of the rotor side projection 42.
- the distance Y, between the second plane 45 a-2 of the swash plate side projection 45 and a similar second plane (not shown) of the swash plate side projection 46 is defined by the swash plate side projection 45, 46.
- the tip is narrower. In other words, in the second plane 45 a-2, the distance between the second flat surface 45 a and the side surface 42 a of the rotor-side protrusion 42 facing the second flat surface 45 a-2 becomes wider toward the tip end of the swash plate-side protrusion 45.
- the swash plate side projection 45 is formed with the second plane 45 a-2, so that the swash plate side projection 45 of the first embodiment which does not have the second plane 45 a-2 is formed.
- the amount of meat is decreasing. That is, in the present embodiment, the second plane 45a-2 forms a lightening portion.
- the inclination angle a of the second plane 45a-2 with respect to the first plane 45a-1 is within a natural range ("> 0 °" and "90 °") for realizing the inclination. Within), there is a suitable range.
- the displacement of the connection P between the 4 5 a-1 and the second plane 4 5 a-2 in the vertical direction on the paper becomes large. For example, even if the second plane 45a-2 is slightly displaced leftward in the drawing, the connection portion P is largely displaced downward in the drawing, and as a result, the first plane 45a-1 is greatly reduced.
- the inclination angle of the second plane 45a-2 with respect to the first plane 45a-1 is 1.
- the angle is set to 2 ° or more, more preferably 2 ° or more.
- the inclination angle of the second plane 45a-2 with respect to the first plane 45a-1 is too large, at least a part of the second plane 45a-2 becomes a cylindrical surface 45b. On the other hand, they are directly connected without going through the convex corners 45c.
- the second plane 45 relative to the first plane 45a-1 is set so that the second virtual plane K2 including the second plane 45a-2 does not intersect the cylindrical surface 45b.
- a ⁇ 2 inclination angle ⁇ is set. That is, in the present embodiment, as shown by the dashed line in FIG.
- the second plane 45a-2 with respect to the first plane 45a-1 is 6 ° or more
- the second plane The virtual plane ⁇ 2 is intersected by the cylindrical surface 4 5 b. Therefore, in the present embodiment, the inclination angle of the second plane 45a-2 with respect to the first plane 45a-1 is set to less than 6 °. Furthermore, if the inclination angle ⁇ is close to 6 °, the connection portion caused by the processing error of the second plane 45 a-2; The probability of intersecting plane 45b is greater. Therefore, the inclination angle of the second plane 45a-2 with respect to the first plane 45a_1 is more preferably set to 3 ° or less.
- the same effects as the effects (5) to (7) are obtained.
- the lightening portion (second plane 45a-2 (the second plane of the side surface 46a is not shown). )
- finish processing to maintain high accuracy of clearance (X-Y) Can be omitted. Therefore, the finishing area for maintaining high accuracy of the clearance (X-Y) can be reduced, and the cost can be reduced.
- a plane (second plane 45a_2) is employed as the lightening portion.
- the swash plate 18 is tilted in a direction different from the direction in which the discharge capacity is changed, and the first surface 45 a of the side surface 45 a of the swash plate side projection 45 a is the side surface 42 of the rotor side projection 42. Even if it is inclined with respect to a, the second surface 45a-2 will be in planar contact with the side surface 42a. Therefore, the tilt of the swash plate 18 relating to the change of the discharge capacity becomes smooth, and good capacity controllability can be maintained. As shown in FIG. 6 and FIG. 7, in the third embodiment, there is provided alignment means 79 for aligning the swash plate 18 with respect to the axis L of the drive shaft 16.
- a ring member 80 as an alignment member is provided on the drive shaft 16 so as to be able to slide along the axis L.
- the ring member 80 is interposed between the spring 36 and the swash plate 18.
- the ring member 80 is pressed against the swash plate 18 by a spring 36.
- 45 is provided at the corner on the swash plate 18 side on the outer peripheral side of the ring member 80.
- a swash plate side guide portion formed of a taper is formed at a portion on the far side and a near side on the paper surface in FIG. 83 are formed (FIG.
- the swash plate-side guide portion 83 has a portion facing the ring side guide portion 8 2 at each value of the inclination angle of the swash plate 18 that changes due to the tilting of the swash plate 18.
- the shape has an inclination angle of 45 ° with respect to the direction.
- the spring 36, the ring member 80 (the ring-side guide portion 82), and the swash plate-side guide portion 83 constitute the centering means 79.
- the ring-side guide portion 8 2 is provided with an arbitrary value of the inclination angle of the swash plate 18,
- the rotor 17 is provided with a projection
- the swash plate 18 is provided with a wall. That is, on the front surface of the swash plate 18, the engagement groove 7 is formed on the side corresponding to the top dead center of the swash plate 18 (the center of the spherical surface of the shoe 25 of the piston 23 located at the top dead center). 0 has been generated.
- the engagement groove 70 is formed by two wall portions 71 and 72 protruding toward the rotor 17 at front and rear positions in the rotation direction on the front surface of the swash plate 18.
- a projection 73 is provided at a position corresponding to the engagement groove 70 in the mouth 17.
- the projecting portion 73 is engaged with the side surface (wall surface) 71 a, 72 a of the wall portion 71, 72, and is engaged with the swash plate 18 with the side surface 73 a.
- Power is transmitted to the side surface 71a of the wall portion 71 (when the rotation direction of the drive shaft 16 is the direction of the arrow R).
- the protrusion ⁇ 3 transmits power to the side surface 72a of the wall portion 72 of the swash plate 18 via the side surface 73b.
- a cam portion 74 as an axial load receiving portion is formed on both sides 73 a and 73 b of the base of the projection 73.
- the convexly curved cylindrical surfaces 7 lb and 7 2 b formed at the tips of the walls 7 1 and 7 2 are movable with respect to the cam surface 7 4 a formed at the rear end surface of the cam 7 4.
- concave portions 75 and 76 are formed at both sides 73a and 73b of the protrusion 73 near the ends of the walls 71 and 72 as a lightening portion.
- the recesses 75, 76 are provided adjacent to the cam portion 74 on the side surfaces 73a, 73b, and are provided on the wall portions 71, 72 associated with the tilting of the swash plate 18 for changing the discharge capacity.
- Each of the cylindrical surfaces 71, 72b has a groove shape extending along the direction of movement relative to the cam surface 74a.
- the concave corners 75 a and 76 a on the cam surface 74 a side in the concaves 75 and 76 are formed in a concave curved shape to reinforce the projection 73.
- the finish for maintaining the accuracy of the clearance high with respect to the tally of the projection 73 between the two walls 71 and 72 is provided.
- the processing area can be reduced.
- the present embodiment has the same effects as the effects (4) to (7). It should be noted that, for example, the following embodiments can be implemented without departing from the spirit of the present invention.
- As a modified example of the first embodiment as shown by a two-dot chain line M in FIG. 4, the sliding surface 4 2 a-1 and the inside of the concave portion 6 1 on the side surface 4 2 a of the port side projection 42.
- Chamfering is performed on the convex corners 42 located on the tip side of the rotor side projections 42 among the convex corners serving as the connection with the non-sliding surface 4 2 a-2. Note that this chamfer is made on the side surface 43 a of the rotor side projection 43 and the convex corner portion 4 serving as a connection portion between the sliding surface 43 a-1 and the non-sliding surface 43 a-2 of the recess 62. 3b (see Figure 2).
- the side surface 45 a of the swash plate side protrusion 45 and the side surface 42 a of the rotor side protrusion 42 are separated by tilting the swash plate side protrusion 45, and the swash plate side
- the side surface 45 a of the projection 45 contacts the convex corner portion 42 b of the rotor side projection 42
- the pressure received by the convex corner portion 42 b from the side surface 45 a of the swash plate side projection 45 is applied.
- a modified example of the fourth embodiment as shown by a two-dot chain line M in FIG.
- the convex corners 73c and 73d on the tip side of the protrusion 73 should be chamfered. Also in this case, even if the convex corners 73c and 73d receive pressure from the side surfaces 71a and 72a of the walls 71 and 72, the pressure is easily dispersed at the protrusion 73. Therefore, the load bearing capacity of the projection 73 can be improved.
- the recesses 61, 62 are formed on the side surfaces 42a, 43a of the rotor-side protrusions 42, 43 at locations other than near the tip of the swash plate-side protrusions 45, 46. It may be provided.
- the lightening portions are formed on the side surfaces 4 2 a and 43 a of the rotor-side projections 42 and 43, and on both sides of the swash-plate side projections 45 and 46. What is necessary is that it is provided on at least one of the four surfaces consisting of the surfaces 45a and 46a.
- the quenching process for the hinge mechanism 19 is not for the entire hinge mechanism 19 but for the hinge mechanism 19 including at least a part of the contact portion between the rotor 17 and the swash plate 18. Any part may be applied to any part.
- the rotor side projections 42, 4 at the tip side (lower side in FIG. 2) of the rotor side projections 42, 43 and the base side of the swash plate side projections 45, 46 are used. Quenching may be applied to the contact point with 3.
- the hinge mechanism 19 only at least a part of the contact point between the rotor 17 and the swash plate 18 is included, and only one side of the rotor 17 and the swash plate 18 is fired.
- a configuration in which the input processing is performed may be used.
- the first embodiment only the wall of the rotor 17 (rotor side projections 42, 43) has a thickness.
- the lightening portion is provided only on the protrusion 44 of the swash plate 18. However, this is changed to a wall portion (rotor side protrusions 42, 43) and a protrusion.
- a lightening portion may be provided in both of the portions 44.
- a lightening portion formed of a recess similar to the recesses 61 and 62 of the first embodiment may be additionally provided at the base of the swash plate side projections 45 and 46.
- the present invention is embodied in a wobbled type variable displacement compressor having a rocking plate as a cam plate.
- the present invention is embodied in a variable displacement compressor of the type having a double-headed piston.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004527365A JPWO2004015269A1 (ja) | 2002-08-07 | 2003-08-07 | 容量可変型圧縮機 |
US10/510,387 US20050147503A1 (en) | 2002-08-07 | 2003-08-07 | Variable displacement compressor |
EP03784588A EP1528256A1 (en) | 2002-08-07 | 2003-08-07 | Variable displacement compressor |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2002-230216 | 2002-08-07 | ||
JP2002230216 | 2002-08-07 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2004015269A1 true WO2004015269A1 (ja) | 2004-02-19 |
Family
ID=31711674
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2003/010094 WO2004015269A1 (ja) | 2002-08-07 | 2003-08-07 | 容量可変型圧縮機 |
Country Status (4)
Country | Link |
---|---|
US (1) | US20050147503A1 (ja) |
EP (1) | EP1528256A1 (ja) |
JP (1) | JPWO2004015269A1 (ja) |
WO (1) | WO2004015269A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR20140000361A (ko) * | 2012-06-22 | 2014-01-03 | 학교법인 두원학원 | 용량가변형 사판식 압축기 |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4626808B2 (ja) * | 2005-04-26 | 2011-02-09 | 株式会社豊田自動織機 | 可変容量型クラッチレス圧縮機用の容量制御弁 |
US7455009B2 (en) * | 2006-06-09 | 2008-11-25 | Visteon Global Technologies, Inc. | Hinge for a variable displacement compressor |
US8118567B2 (en) * | 2006-12-15 | 2012-02-21 | Kabushiki Kaisha Kawasaki Precision Machinery | Swash plate type piston pump motor |
CN106460816B (zh) * | 2014-06-27 | 2018-12-07 | 法雷奥日本株式会社 | 可变容量斜板式压缩机 |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5231914A (en) * | 1990-09-14 | 1993-08-03 | Hitachi, Ltd. | Variable displacement compressor |
US5370503A (en) * | 1992-05-08 | 1994-12-06 | Sanden Corporation | Swash plate type compressor with variable displacement mechanism |
JPH0814159A (ja) * | 1994-06-27 | 1996-01-16 | Sanden Corp | 斜板式可変容量圧縮機 |
US5785503A (en) * | 1995-11-24 | 1998-07-28 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Variable displacement compressor |
US20010031205A1 (en) * | 2000-04-18 | 2001-10-18 | Masaki Ota | Compressors |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2000145653A (ja) * | 1998-11-12 | 2000-05-26 | Toyota Autom Loom Works Ltd | 可変容量型圧縮機 |
WO2005024233A1 (ja) * | 2003-09-02 | 2005-03-17 | Kabushiki Kaisha Toyota Jidoshokki | 容量可変型斜板式圧縮機 |
-
2003
- 2003-08-07 WO PCT/JP2003/010094 patent/WO2004015269A1/ja not_active Application Discontinuation
- 2003-08-07 JP JP2004527365A patent/JPWO2004015269A1/ja active Pending
- 2003-08-07 US US10/510,387 patent/US20050147503A1/en not_active Abandoned
- 2003-08-07 EP EP03784588A patent/EP1528256A1/en not_active Withdrawn
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5231914A (en) * | 1990-09-14 | 1993-08-03 | Hitachi, Ltd. | Variable displacement compressor |
US5370503A (en) * | 1992-05-08 | 1994-12-06 | Sanden Corporation | Swash plate type compressor with variable displacement mechanism |
JPH0814159A (ja) * | 1994-06-27 | 1996-01-16 | Sanden Corp | 斜板式可変容量圧縮機 |
US5785503A (en) * | 1995-11-24 | 1998-07-28 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Variable displacement compressor |
US20010031205A1 (en) * | 2000-04-18 | 2001-10-18 | Masaki Ota | Compressors |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR20140000361A (ko) * | 2012-06-22 | 2014-01-03 | 학교법인 두원학원 | 용량가변형 사판식 압축기 |
KR101907696B1 (ko) * | 2012-06-22 | 2018-10-15 | 학교법인 두원학원 | 용량가변형 사판식 압축기 |
Also Published As
Publication number | Publication date |
---|---|
EP1528256A1 (en) | 2005-05-04 |
JPWO2004015269A1 (ja) | 2005-12-02 |
US20050147503A1 (en) | 2005-07-07 |
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