JPWO2019176724A1 - Slanted plate compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a swash plate compressor having excellent reliability by suppressing generation of noise in a thrust bearing in a swash plate compressor. Another object of the present invention is to provide a swash plate compressor provided with a thrust bearing, which is a simple mechanism having a small number of parts and few adverse effects on assembly. SOLUTION: In the one-sided slanted plate compressor 1 of the present invention, spur bearings 201 and 202 are adopted as thrust bearings, and the spur bearings are fixed to a front housing 5 or a rotor 191. The spur bearings 201 and 202 are made of either a resin, a metal sintered material, or a ceramics sintered material. Further, the spur bearing 202 has a gradient α in which the thickness of the spur bearing 202 corresponding to the top dead center side of the piston 25 is small and the thickness of the spur bearing 202 corresponding to the bottom dead center side of the piston 25 is large. [Selection diagram] Fig. 3

Description

The present invention relates to a swash plate compressor, particularly a swash plate compressor suitable for a vehicle air conditioning system.

A vane type compressor, a scroll type compressor, a swash plate type compressor, and the like are used in the air conditioning system of the vehicle. In particular, the swash plate compressor has excellent performance and reliability, and is widely used as a compressor that utilizes the power from the engine of a vehicle.

A variable capacity single-sided sloping plate compressor for vehicles will be described with reference to FIG. The one-sided swash plate compressor 1 includes a cylinder block 2, a rear head 4 assembled on the rear side (right side in the figure) of the cylinder block 2 via a valve plate 3, and a front side (in the figure, in the figure) of the cylinder block 2. It has a front housing 5 assembled so as to close the left side), and the housing 7 is formed by fastening these housing members in the axial direction with a fastening bolt 6.

At the front end of the compressor 1, a drive pulley 9 is rotatably supported by a boss portion 8 of the front housing 5 via a bearing 10 from a vehicle engine (not shown) via a belt (not shown). The rotational power transmitted to the drive pulley 9 is transmitted to the shaft 11.

The shaft 11 is rotatably supported via a radial bearing 17 provided in the front housing 5 and a radial bearing 18 housed in the cylinder block 2.

A disc-shaped rotor 19 is fixed to the shaft 11. Further, the shaft is provided with a swash plate 23 that can be tilted, and the rotational power transmitted to the rotor 19 is transmitted to the swash plate 23 via the link member 21 connected to the rotor 19, and the rotor 19 The swash plate 23 swings and rotates with the rotation. The oscillating rotation of the swash plate 23 is transmitted to the piston 25 via a pair of shoes 24 provided on the peripheral edge portion of the swash plate 23. The piston 25 is housed in a cylinder bore 26 formed in the cylinder block 2.

When the shaft 11 rotates, the swash plate 23 swings and rotates accordingly, and the swing rotation motion of the swash plate 23 is converted into a reciprocating linear motion of the piston 25 via the shoe 24, and the piston 25 in the cylinder bore 26. The volume of the compression chamber 27 formed between the valve plate 3 and the valve plate 3 is increased or decreased, and the working fluid is sucked, compressed, and discharged through the suction hole 29 and the discharge hole 31 formed in the valve plate 3.

Further, a thrust bearing 20 is provided between the rotor 19 and the front housing 5. The compression reaction force in the thrust direction due to the compression of the working fluid is transmitted from the piston 25 to the rotor 19 via the swash plate 23 and the link member 21, and is supported by the front housing 5 via the thrust bearing 20.

As shown in FIG. 2, as a thrust bearing 20 that receives a load in the thrust direction, a rolling bearing 20-2 that uses a plurality of rollers as rolling elements is known. The rolling bearing 20-2 is sandwiched between the front housing 5 side thrust trace 20-3 and the rotor 19 side thrust trace 20-1. The rolling bearing can receive a high load from the rotating rotor 19 even in a poorly lubricated environment, which is advantageous in terms of reliability.

However, in the one-sided slanted plate compressor, an eccentric load acts on the thrust bearing 20 that receives the compression reaction force due to the highest pressure in the cylinder bore at the top dead center of the piston. Since this eccentric load rotates with the rotation of the rotor 19, among the plurality of rollers of the thrust bearing 20, the roller that supports the high load and the roller that receives the low load change according to the rotation position of the rotor 19, and the rollers vibrate. Induce. The vibration of the rollers propagates to the front housing 5 to increase the vibration and noise of the compressor 1, and also becomes a factor of impairing the reliability of each component constituting the thrust bearing.

As a means for solving the above-mentioned problems, a compressor has been proposed in which a shaft is held in a housing and a slide bearing is provided between a rotor fixed to the shaft and an inner surface of the housing (Patent Document 1). In this slide bearing, a plurality of hemispherical bearing elements having a spherical shape on the side facing the housing and a planar shape on the side facing the rotor are held in a plurality of spherical recesses formed on the inner surface of the housing. It is composed of. With such a configuration, the rolling noise peculiar to the rolling bearing is suppressed. Further, since the plurality of bearing elements held in the spherical recess can rotate in response to the change in the direction of the force, the eccentric load based on the compression fluctuation can be alleviated.

However, the slide bearing described in Patent Document 1 also has the following problems. That is, in the slide bearing described in Patent Document 1, a plurality of hemispherical bearing elements are arranged in a plurality of spherical recesses formed on the inner surface of the housing, and the spherical recesses in which lubricating oil does not easily enter rotate the bearing elements. There is a risk of wear due to sliding friction caused by the bearing. Further, since a plurality of bearing elements are required, there is a possibility that the number of parts increases and the assembly cost increases, or the rotor is assembled in a state where the bearing elements are not securely held in the spherical recess.

JP-A-9-209925

The present invention has been made in view of the circumstances described in the above background technology, and an object of the present invention is to suppress the generation of noise in a thrust bearing in a swash plate compressor and to provide a swash plate compressor having excellent reliability. There is. Another object of the present invention is to provide a swash plate compressor provided with a thrust bearing mechanism, which is a simple mechanism having a small number of parts and few adverse effects on assembly.

The compressor according to the present invention includes a housing, a shaft rotatably supported in the housing through a crank chamber, and a rotor fixed to the shaft and having a thrust surface orthogonal to the rotation axis of the shaft. Between the swash plate that rotates in synchronization with the rotor, the piston that reciprocates in the cylinder bore formed in the cylinder block as the swash plate rotates, and the inner wall of the housing and the thrust surface of the rotor. It is characterized by including a spur bearing to be arranged and a mechanism for fixing the spur bearing to the thrust surface. Here, the plain bearing is a so-called slide bearing that does not use a rolling member. Further, here, "fixed" means that the spur bearing is attached so as not to rotate or move relatively, and is not limited to the meaning of being physically restrained.

Further, the compressor according to the present invention includes a housing, a shaft rotatably supported through the crank chamber in the housing, and a thrust surface fixed to the shaft and orthogonal to the rotation axis of the shaft. A rotor, a swash plate that rotates in synchronization with the rotor, a piston that reciprocates due to the rotation of the swash plate, a spur bearing arranged between an inner wall of the housing and the thrust surface of the rotor, and the above. It is characterized in that it is provided with a mechanism for fixing the spur bearing to the inner wall of the housing.

As described above, the swash plate compressor of the present invention is characterized in that the spur bearing is fixed to the inner wall of the rotor or the housing, and this fixing limits the sliding surface of the spur bearing. It is possible to reduce wear, improve the followability of the rotor and the sliding surface of the housing, and obtain a swash plate compressor with excellent quietness that does not generate vibration and noise associated therewith.

The mechanism for fixing the spur bearing is not particularly limited, and a general fixing mechanism can be used. For example, a method of joining on a surface using an adhesive or welding, a method of fitting, inserting, or screwing a convex portion and a concave portion using a pin or a screw to physically fix the convex portion and the concave portion is used. However, from the viewpoint of fixing strength in the rotation direction and easy mounting, a method of fitting the convex portion and the concave portion is preferable.

Further, it is more preferable that the spur bearing of the swash plate compressor of the present invention is provided with a thrust trace between the inner wall of the housing and the spur bearing in the thrust bearing mechanism fixed to the thrust surface of the rotor. Further, in the thrust bearing mechanism in which the flat bearing of the swash plate compressor of the present invention is fixed to the inner wall of the housing, it is more preferable that a thrust trace is provided between the flat bearing and the thrust surface of the rotor. Further, in the former case, it is more preferable that the thrust trace is fixed to the inner wall of the housing, and in the latter case, to the thrust surface of the rotor.

Further, it is more preferable that the spur bearing in the thrust bearing mechanism of the swash plate compressor of the present invention has a gradient in the thickness direction. By forming a deviation in the thickness direction of the spur bearing, it is possible to disperse the eccentric load on the thrust bearing mechanism in which the compressive reaction force generated by the compressible fluid is generated. As a result, uneven wear of each component of the thrust bearing mechanism can be reduced, and vibration and the generation of noise associated therewith can be suppressed.

Even more preferably, the shape of the spur bearing, that is, the deviation in the thickness direction forms a gradient in the plane, and the gradient corresponds to the thickness of the spur bearing corresponding to the top dead center side of the piston. It is desirable that the slope is small and the thickness of the spur bearing corresponding to the bottom dead center side of the piston increases.

Specifically, when the thickness direction of the spur bearing is horizontal and a gradient of 89.90 to 89.99 ° is formed in the plane of the spur bearing, an excellent effect is exhibited, but 89.93 to 89 A better effect is exhibited when a gradient of .97 ° is formed.

The materials of the spur bearing and the thrust trace constituting the thrust bearing mechanism of the swash plate compressor of the present invention are preferably a resin, a metal sintered material, or a ceramics sintered material.

As the resin, PEEK (Polyethertherketone), PPS (Polyphenylene sulfide), aromatic polyamide (Aromatic polyamide), polyimide (Polyimide), POM (Polyacetal), PTFE (Polyethylene) resin, etc. can be used. Further, glass fiber, carbon fiber, stainless fiber, cellulose nanofiber (CNF) and the like may be blended with these resins. From the viewpoint of processing accuracy, it is preferable that these resins are used for processing by an injection molding method or an RIM (Reaction injection molding) molding method.

The metal sintering material is preferably a material formed by a powder metallurgy molding method of metal powder and alloy powder generally used for bearings. In particular, it is preferable to use iron-based alloy powder or copper-based alloy powder.

Ceramic is more expensive than metal because it exhibits better performance than metal in terms of slidability, wear resistance, etc., but it is suitable for bearing mechanism parts that pursue performance. The ceramic sintered material is preferably a material formed by a powder metallurgy molding method using powders such as metal oxides, metal carbides, metal borides, and metal nitrides.

Such a metal sintering material and a ceramic sintering material may be a composite sintering material, respectively, and carbon fiber, stainless fiber, graphite powder and the like can be blended. In particular, since the sintered material is a porous body and can hold a lubricant, it is possible to provide a thrust bearing mechanism with less friction and wear without requiring a special lubricating device. It is preferable because of its characteristic.

As described above, the thrust bearing mechanism of the swash plate compressor of the present invention is simple as well as reducing vibration and accompanying noise by fixing the spur bearing to the thrust surface of the rotor or the inner wall of the housing. It is possible to provide a thrust type compressor having a structure and excellent reliability.

It is sectional drawing which shows the structure of the one-sided diagonal plate type compressor for a general vehicle. It is a partial decomposition schematic perspective view for demonstrating the conventional thrust bearing mechanism. It is a partial decomposition schematic perspective view for demonstrating the mechanism which the spur bearing is fixed to the thrust surface of a rotor in the swash plate type compressor which is one Embodiment of this invention. It is a partial decomposition schematic perspective view for demonstrating the mechanism which the planor bearing is fixed to the thrust surface of the rotor using the thrust trace in the swash plate type compressor which is one Embodiment of this invention. It is a schematic plan view (a) and the schematic sectional view (b) for demonstrating the structure of the inclined plan head bearing provided with the convex part in the swash plate type compressor which is one Embodiment of this invention.

Hereinafter, the present invention will be described in more detail using one embodiment, but the present invention is not limited to this, and various modifications may be made without departing from the gist of the present invention. It is possible and limited only by the technical ideas described in the claims.

FIG. 1 is a schematic cross-sectional view showing the structure of a general one-sided slanted plate compressor 1 for vehicles. The swash plate compressor of the present invention has the same structure as that shown in FIG. 1 and the background technology, except for 20-1, 20-2, and 20-3 that constitute the thrust bearing 20 of the rolling bearing.

FIG. 3 is a partially disassembled schematic perspective view of the thrust bearing mechanism in the swash plate compressor 1 according to the embodiment of the present invention. A rotor 191 is fixed to the shaft 11 by shrink fitting or press fitting. The rotor 191 includes a disk portion 191a, a pair of link arm portions 191b projecting from the outer peripheral edge of the disk portion 191a to the rear side, and a pair of link arm portions 191b in the circumferential direction of the outer peripheral edge of the disk portion 191a. It is composed of a balance weight portion 191c provided on the opposite side of the above.

The swash plate 23 is connected to the link arm 191b of the rotor 191 via the link member 21. The piston 25, which engages with the disk portion of the swash plate 23 via the shoe 24, reciprocates in the cylinder bore 26 as the swash plate 23 swings, and the relative positions in the rotation direction with the link arm 191b coincide with each other. Sometimes it reaches the top dead center position. That is, the link arm 191b corresponds to the top dead center position where the compression reaction force of the piston 25 is the largest.

An annular thrust surface 191d orthogonal to the rotation axis of the shaft 11 is formed on the front housing 5 side of the disk portion 191a of the rotor 191. Further, a recess 191e is formed on the inner peripheral side of the thrust surface 191d. In this example, recesses 191e are provided on the back side of the portion where the pair of link arms 191b are provided and on the back side of the portion where the balance weight 191c is provided.

A ring-shaped spur bearing 201 is provided between the thrust surface 191d of the rotor 191 and the inner wall of the front housing 5. The spur bearing 201 is formed with a convex portion 201a provided so as to project toward the inner peripheral side. The convex portions are provided at two positions with different phases by 180 °, and the spur bearing 201 is formed on the rotor 191 by fitting the convex portions 201a with the concave portions 191e formed on the inner peripheral side of the thrust surface 191d. It is attached, that is, fixed to the thrust surface 191d so that it cannot rotate relative to the thrust surface 191d.

The spur bearing 201 is formed by injection molding a resin material such as super engineering plastic. As a material, for example, PEEK (Polytheretherketone), PPS (Polyphenylene sulfide), aromatic polyamide (Aromatic polyamide), polyimide (Polyimide), POM (Polyacetal), PTFE (Polyethylene) resin, etc. can be used. .. Further, glass fiber, carbon fiber, stainless fiber, cellulose nanofiber (CNF) and the like may be blended with these resins. By molding the spur bearing 201 with such a resin, high reliability is ensured in each stage as compared with a normal resin, and a complicated shape such as a convex portion 201a is injection-molded without cutting. Can be formed by

As another example of forming the spur bearing 201, it is also possible to mold it with a metal sintered material such as tin bronze powder containing about 3 to 10% tin. By forming a spur bearing with such a metal sintered material, it is possible to form a complicated shape and to use it for use with a high load.

FIG. 3 shows a case where the spur bearing 201 is fixed to the thrust surface 191d of the rotor 191. However, as one embodiment, the same spur bearing 201 is used, and the rotor 191 is mounted on the inner wall surface of the front housing 5. A thrust bearing mechanism having the same recess as the recess formed on the thrust surface 191d may be configured, and the spur bearing 201 may be fixed to the inner wall of the front housing 5. In this case as well, the same effect as that of the thrust bearing mechanism of FIG. 3 can be obtained.

FIG. 4 is a partial decomposition schematic perspective view of a thrust bearing function using a thrust trace in the swash plate compressor 1 according to the embodiment of the present invention. Here, a mechanism in which the spur bearing 201 is fixed to the thrust surface 191d of the rotor 191 which is the same as in FIG. 3 is used, and a thrust trace 201-1 for improving the slidability of the front housing 5 and the spur bearing 201 is further provided. It is inserted.

Such a thrust trace 201-1 can also be applied to a case where the same recess as the recess 191e formed on the thrust surface 191d of the rotor 191 is formed on the inner wall surface of the front housing 5 to fix the spur bearing 201 to the front housing 5. In that case, the thrust trace 201-1 of FIG. 4 will be inserted between the rotor 191 and the spur bearing 201.

Further, the thrust trace 201-1 is fixed to the housing 7 when the spur bearing 201 is fixed to the rotor 191 and to the thrust surface 191d of the rotor 191 when the spur bearing 201 is fixed to the housing 7. Is preferably done.

FIG. 5 shows a preferable shape of a spur bearing used for a thrust bearing mechanism in the swash plate compressor 1 according to the embodiment of the present invention. 5 (a) is a schematic plan view showing the structure of the inclined flat bearing 202 having a gradient formed on the plan bearing 201 having the convex portion shown in FIG. 3, and FIG. 5 (b) is a schematic plan view of FIG. 5 (b). It is a schematic cross-sectional view (b) in the cutting line I of a).

In the inclined flat bearing 202, the thickness of the flat bearing 202 on the side corresponding to the top dead center of the piston 18 is small, and the thickness of the flat bearing 202 on the side corresponding to the top dead center of the piston is large in the thickness direction. It has a gradient α. In this example, with the thickness direction of the spur bearing 202 as the horizontal direction, a gradient α of 89.95 ° is formed in the plane of the spur bearing 202.

As described above, the link arm 191b of the rotor 191 corresponds to the top dead center position where the compression reaction force is the largest. A convex portion 202a is integrally formed on the inclined flat bearing 202, and by fitting the convex portion 202a into the concave portion 191e of the rotor 191 to correspond to the top dead center side having a high compressive reaction force, that is, the link arm 191b. The tilted spur bearing 202 can be mounted by being reliably positioned so that the thickness of the slanted spur bearing 202 on the side to be tilted is reduced. With such a configuration, it is possible to weaken the contact surface pressure between the inclined flat bearing 202 and the inner wall surface of the front housing 5 which is in sliding contact with the inclined flat bearing 202 in the region on the top dead center side where the compression reaction force is high. The eccentric load on the entire sliding surface can be relaxed.

The gradient α in the thickness direction of the inclined plan bearing 202 can be formed by cutting, but if sufficient accuracy can be obtained in injection molding or sintering molding, the cutting step can be omitted. is there.

The inclined spur bearing 202 shown in FIG. 5 can also be applied to the thrust bearing mechanism using the thrust trace shown in FIG. In this case, the spur bearing 201 may be replaced with the inclined spur bearing 202 while leaving the thrust trace 201-1 shown in FIG. With such a configuration, in the region on the top dead center side where the compression reaction force is high, the contact between the inclined flat bearing 202 and the thrust trace 2011-1 fixed to the inner wall surface of the front housing 5 which is in sliding contact with the inclined flat bearing 202. The surface pressure can be weakened, and the eccentric load on the entire sliding surface can be alleviated.

The swash plate compressor provided with the thrust bearing mechanism shown in FIG. 3 or 4 that employs such an inclined flat bearing causes further vibration due to the uniform eccentric load received by the front housing 5 via the thrust bearing. The amount of noise is small, the noise associated with the vibration can be further improved, the slidability of the thrust bearing mechanism is improved, and a swash plate compressor having excellent durability can be obtained.

1 One-sided thrust type compressor 2 Cylinder block 3 Valve plate 4 Rear head 5 Front housing 6 Fastening bolt 7 Housing 8 Boss part 9 Drive pulley 10 Bearing 11 Shaft 17 Radial bearing 18 Radial bearing 19 Rotor 19a Disc 19b Link arm 19c Balance Weight part 19d Thrust surface 191 Rotor 191a Disc part 191b Link arm part 191c Balance weight part 191d Thrust surface 191e Concave 20 Thrust bearing 20-1 Thrust bearing 20-2 Needle bearing 20-3 Thrust trace 201 Flat bearing 201a Convex part 201- 1 Thrust trace 202 Tilted spur bearing 202a Convex α Gradient of slanted spur bearing
21 Link member 22 Hinge ball (sleeve)
23 Swash plate 24 Shoe 25 Piston 26 Cylinder bore 27 Compression chamber 28 Suction valve 29 Suction hole 30 Discharge valve 31 Discharge hole 32 Suction chamber 33 Discharge chamber 34 Crank chamber I Cutting line

Claims (9)

With the housing
A shaft that is rotatably supported through the crank chamber in the housing,
A rotor fixed to the shaft and having a thrust surface orthogonal to the rotation axis of the shaft,
A swash plate that rotates in synchronization with the rotor,
A piston that reciprocates in the cylinder bore formed in the cylinder block as the swash plate rotates,
A spur bearing arranged between the inner wall of the housing and the thrust surface of the rotor,
A swash plate compressor comprising a mechanism for fixing the spur bearing to the thrust surface. With the housing
A shaft that is rotatably supported through the crank chamber in the housing,
A rotor fixed to the shaft and having a thrust surface orthogonal to the rotation axis of the shaft,
A swash plate that rotates in synchronization with the rotor,
A piston that reciprocates due to the rotation of the swash plate,
A spur bearing arranged between the inner wall of the housing and the thrust surface of the rotor,
A swash plate compressor characterized in that a mechanism for fixing the spur bearing to the inner wall of the housing is provided. In the swash plate compressor according to claim 1,
A swash plate compressor characterized in that a thrust trace is provided between an inner wall of the housing and the spur bearing. In the swash plate compressor according to claim 1,
A swash plate compressor characterized in that a thrust trace fixed to the inner wall of the housing is provided between the inner wall of the housing and the spur bearing. In the swash plate compressor according to claim 2,
A swash plate compressor characterized in that a thrust trace is provided between the thrust surface of the rotor and the spur bearing. In the swash plate compressor according to claim 2,
A swash plate compressor characterized in that a thrust trace fixed to the thrust surface is provided between the thrust surface and the spur bearing. In the swash plate compressor according to any one of claims 1, 3 and 4.
The spur bearing is a flat plate having a shape consistent with the thrust surface, and is a swash plate compressor characterized by having a gradient in the thickness direction. In the swash plate compressor according to claim 7,
With respect to the gradient in the thickness direction of the spur bearing, the thickness of the spur bearing corresponding to the top dead center side of the piston is small, and the thickness of the spur bearing corresponding to the bottom dead center side of the piston is large. A swash plate compressor characterized by having a gradient. In the swash plate compressor according to any one of claims 1 to 8,
A swash plate compressor characterized in that the spur bearing is made of either a resin, a metal sintered material, or a ceramics sintered material.

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