JP5938217B2 - Compressor plain bearings and compressors - Google Patents

Description

  The present invention relates to a sliding bearing for a compressor that rotatably supports a rotating member for driving a compression mechanism of the compressor, and a compressor including the sliding bearing for the compressor.

  A compressor used in an air conditioner or the like has a rotating member for driving the compression mechanism, and the rotating member is supported by a bearing. Conventionally, for example, in a compressor provided with a sliding bearing that rotatably supports this rotating member, a material in which a fluororesin is coated on the base material through a porous metal having a solid lubricating function has been proposed as the sliding bearing. (See Patent Document 1). This sliding bearing is formed by coating the surface of a flat plate member with a fluororesin via a bronze sintered layer that is a porous metal and bending it into a cylindrical shape.

  In Patent Document 1, since a sliding bearing is employed as a bearing that supports a rotating member, the number of components is reduced as compared with the case where a rolling bearing is employed, and the cost can be reduced. In addition, the interposition of the fluororesin and the porous metal makes it difficult for the sliding contact portion between the rotating member and the sliding bearing to be worn, thereby extending the life of the compressor. Since the fluororesin is coated on the base material through the porous metal, the fluororesin is hardly peeled off from the base material side when a part of the fluororesin enters the hole portion of the porous metal.

  The sliding bearing that supports the rotating member for driving the compression mechanism has precise rotation accuracy and stably obtains low rotational torque, so it has excellent load resistance and creep resistance, and is dimensioned even under high surface pressure. It is required that it does not change. As a slide bearing used for the same application, in addition to Patent Document 1, for example, a multilayer bearing disclosed in Patent Document 2 and Patent Document 3 can be cited. The bearing (sliding member) of Patent Document 2 has a surface layer made of a polyether ether ketone (hereinafter referred to as PEEK) resin on a porous sintered layer on a back metal layer. In the cylindrical bearing bush in Patent Document 3, the bronze sintered layer and the synthetic resin composition filled and coated on this layer are exposed on the inner peripheral surface thereof.

JP 2002-349437 A JP-A-8-210357 JP 2007-205254 A

  The sliding bearing described in Patent Document 2 has a manufacturing process in which a lead bronze powder is dispersed to a thickness of 0.3 mm on a 0.8 mm-thick back metal plated with copper and sintered to be porous. A sintered layer is formed, a sheet of a resin composition mainly composed of PEEK resin is superimposed on the porous sintered layer, and pressed between the rolls to impregnate and coat the resin composition. 5 mm multi-layered and further cut, then the resin composition side facing inward, for example, into a cylindrical shape with an inner diameter of 20 mm and a width of 20 mm, and then the inner diameter becomes a perfect circle by lathe or polishing It is manufactured by finishing so as to be. The same applies to the sliding bearings in Patent Document 1 and Patent Document 3, such as bending into a cylindrical shape (cylindrical shape) after forming and cutting the multilayer.

  For this reason, as shown in FIG. 3 of Patent Document 3, a cutting portion remains in one place in the circumferential direction of the sliding bearing, and the shape in the vicinity of the cutting portion becomes distorted even if processed with a lathe or a polishing machine. There is a problem. Further, in the case of lathe processing, there is a problem in that the cutting tool is heavily worn by the cutting tool and the required time is increased. Also in the case of polishing, since the object to be polished is a resin, there is a problem that the grindstone is frequently clogged, and the required time is also increased.

  The present invention has been made in order to cope with such problems, and is easy to manufacture, has high dimensional accuracy, and has heat resistance, low friction, wear resistance, load resistance, load resistance, and the like. An object of the present invention is to provide a sliding bearing for a compressor that has excellent creep properties and can stably obtain a low rotational torque, and a compressor including the sliding bearing for a compressor.

  A sliding bearing for a compressor according to the present invention is a sliding bearing for a compressor that rotatably supports a rotating member for driving a compression mechanism of the compressor, and the sliding bearing is formed on a sintered metal substrate, It has a sliding surface of a resin layer made of a resin composition based on an aromatic polyetherketone resin, and the resin layer has a surface of 0.1 to 0.7 mm on the surface of the sintered metal substrate. It is characterized in that it is provided integrally by being laminated by injection molding with a thickness.

  The resin composition includes a fibrous filler, and in the resin layer, the fibrous filler is oriented so that the length direction of the fiber intersects 45 to 90 degrees with respect to the sliding direction of the sliding bearing. It is characterized by being.

  The thickness of the resin layer is 1/8 to 1/2 of the thickness of the sintered metal substrate.

  The sintered metal base material has a theoretical density ratio of 0.7 to 0.9. Further, the sintered metal substrate is made of a sintered metal containing iron as a main component.

  An average fiber length of the fibrous filler is 0.02 to 0.2 mm. The fibrous filler is a carbon fiber. In particular, the carbon fiber is a PAN-based carbon fiber.

The resin composition includes 5 to 30% by volume of the carbon fiber and 1 to 30% by volume of a polytetrafluoroethylene (hereinafter referred to as PTFE) resin with respect to the entire resin composition. The resin composition is a resin composition having a melt temperature of 50 to 200 Pa · s at a resin temperature of 380 ° C. and a shear rate of 1000 s ⁻¹ .

  The sliding bearing is a bearing that supports the rotating member in a radial direction (radial sliding). The radial plain bearing is arranged so as to pressure-isolate an internal space in the housing of the compression mechanism.

  The sliding bearing is a bearing that supports the rotating member in a thrust direction (thrust sliding). In addition, the thrust slide bearing is disposed on a side that receives a compression reaction force generated in the compression mechanism via the rotating member.

  A compressor according to the present invention includes the above-described plain bearing according to the present invention, which rotatably supports a rotating member for driving a compression mechanism.

  The sliding bearing for a compressor of the present invention has a sliding surface of a resin layer made of a resin composition having an aromatic polyether ketone resin as a base resin on a sintered metal base material, so that it has heat resistance and low friction. There is an advantage that it becomes a slide bearing for a compressor excellent in heat resistance and wear resistance. In addition, since the resin layer is integrally provided by injection molding on the surface of the sintered metal substrate with a thickness of 0.1 to 0.7 mm, it is excellent in load resistance and creep resistance. It is possible to stably obtain a low rotational torque without changing the dimensions even under high surface pressure. Furthermore, the resin layer is provided integrally with the surface of the sintered metal base material by injection molding, that is, the resin metal layer is formed by injection molding by inserting the sintered metal base material into the mold. Unlike conventional multi-layer bearings, there is no need to cut or bend the lathe with a lathe or grinding machine after multi-layer formation and cutting, and manufacturing is easy and low cost, but the sliding surface has high dimensional accuracy. It becomes.

  Since a fibrous filler is included in the resin composition, the heat resistance, wear resistance, load resistance, and creep resistance of the resin layer can be further increased. Furthermore, since the fibrous filler in the resin layer is oriented so that the length direction of the fiber intersects 45 to 90 degrees with respect to the sliding direction of the sliding bearing, Aggressiveness to the mating material surface can be reduced, and fluctuations in rotational torque can be prevented.

  Since the thickness of the resin layer is 1/8 to 1/2 of the thickness of the sintered metal base material, the heat generated by frictional heat easily escapes from the friction surface to the sintered metal base material and is difficult to store heat. Furthermore, it becomes a slide bearing for a compressor excellent in heat resistance, low friction and wear resistance.

  Since the theoretical density ratio of the sintered metal base material is 0.7 to 0.9, it has the required denseness to ensure the bearing strength that the sintered metal base material bears, and the resin layer is sintered. Unevenness on the surface for firmly adhering to the base material made of sintered metal can be secured. It is also possible to hold the lubricating oil on the sintered metal substrate. Furthermore, the thermal conductivity of the sintered metal substrate can be ensured.

  Since the sintered metal substrate is made of a sintered metal containing iron as a main component, higher bearing strength can be obtained.

  Since the average fiber length of the fibrous filler contained in the resin composition forming the resin layer is 0.02 to 0.2 mm, the resin layer has excellent frictional wear characteristics and creep resistance, and has a thin moldability. Without hindering, the resin layer can be easily laminated on the surface of the sintered metal substrate with a thickness of 0.1 to 0.7 mm by injection molding.

  Since the fibrous filler is carbon fiber, the reinforcing effect, abrasion resistance, and low friction properties of the resin layer are particularly excellent. Moreover, by using PAN-based carbon fiber among carbon fibers, the elastic modulus of the resin layer is increased, and deformation and wear of the resin layer are reduced. Furthermore, the true contact area of the friction surface is reduced, and frictional heat generation is also reduced.

  Since the resin composition forming the resin layer contains 5 to 30% by volume of carbon fiber and 1 to 30% by volume of PTFE resin as a fibrous filler with respect to the entire resin composition, even under high PV conditions, The deformation and wear of the resin layer, the aggressiveness to the mating material surface are small, and the resistance to oil and the like is high.

Since the resin composition forming the resin layer is a resin composition having a melt temperature of 50 to 200 Pa · s at a resin temperature of 380 ° C. and a shear rate of 1000 s ⁻¹ , 0.1 to 0 is formed on the surface of the sintered metal substrate. .7mm thin insert molding can be performed smoothly.

  The sliding bearing for a compressor of the present invention is excellent in wear resistance, low friction, dimensional stability, etc., while having the same bearing size as a conventional sliding bearing for a compressor. For this reason, it can be used suitably for the radial sliding bearing which supports the rotating member of a compressor in a radial direction. In addition, there is no cutting part like a conventional sliding bearing for a compressor, and the outer peripheral surface and sliding surface of the bearing can be formed with high accuracy, so that the fitting clearance with the support shaft can be reduced, and the good Sealing performance can be demonstrated. For this reason, it is also possible to arrange | position the internal space in the housing of a compressor so that it may isolate in pressure, without providing a sealing member.

  Although it is the same bearing size as the conventional sliding bearing for a compressor of the present invention, it is excellent in wear resistance, low friction, dimensional stability, and the like. For this reason, it can be used conveniently also as a thrust slide bearing which supports the rotation member of a compressor in a thrust direction.

  The compressor of the present invention is a compressor provided with a sliding bearing that rotatably supports a rotating member for driving a compression mechanism, and the sliding bearing for a compressor of the present invention is adopted as this sliding bearing. The compressor can be excellent in energy saving and long life.

It is sectional drawing which shows 1st Embodiment of the compressor using the sliding bearing for compressors of this invention. It is the perspective view and sectional drawing which show an example of the sliding bearing for compressors of this invention (radial sliding bearing). It is the perspective view and sectional drawing which show the other example of the sliding bearing (radial sliding bearing) for compressors of this invention. It is sectional drawing which shows 2nd Embodiment of the compressor using the sliding bearing for compressors of this invention. It is the perspective view and sectional drawing which show an example of the sliding bearing (thrust sliding bearing) for compressors of this invention. It is sectional drawing which shows 3rd Embodiment of the compressor using the sliding bearing for compressors of this invention. It is sectional drawing which shows 4th Embodiment of the compressor using the sliding bearing for compressors of this invention.

  As a first embodiment of a compressor using a sliding bearing for a compressor of the present invention, an example of a single-headed piston compressor constituting a vehicle air conditioner will be described with reference to FIG.

  As shown in FIG. 1, the compressor 5 includes a cylinder block 6, a front housing 7, and a rear housing 9 that constitute the housing. The rear housing 9 is joined and fixed to the cylinder block 6 via the valve forming body 8. Here, the crank chamber 10 is located in a portion surrounded by the cylinder block 6 and the front housing 7. A drive shaft 11 is rotatably supported by the housing so as to penetrate the crank chamber 10. The drive shaft 11 is made of metal or the like. One end side (left side in the figure) of the drive shaft 11 is directly connected to the vehicle engine via a power transmission mechanism. An iron lug plate 12 is fixed to the drive shaft 11 in the crank chamber 10 so as to be integrally rotatable. The drive shaft 11 and the lug plate 12 constitute a rotating member.

  One end of the drive shaft 11 is rotatably supported by a radial sliding bearing 1a fitted in a through hole 7a provided in the front housing 7. The other end of the drive shaft 11 is rotatably supported by a radial slide bearing 1 b fitted in a through hole 6 a provided in the cylinder block 6. The radial sliding bearings 1a and 1b are the sliding bearings for the compressor of the present invention.

  The crank chamber 10 accommodates a swash plate 13 as a cam plate. The swash plate 13 can be rotated synchronously with the lug plate 12 and the drive shaft 11 by the operation connection with the lug plate 12 via the hinge mechanism 14 and the support of the drive shaft 11, and in the direction of the rotation center axis of the drive shaft 11. It is configured to be tiltable with respect to the drive shaft 11 while being accompanied by the sliding movement. A plurality of cylinder bores 15 are formed in the cylinder block 6, and a single-headed piston 16 is accommodated in the cylinder bore 15 so as to be capable of reciprocating. The front and rear openings of the cylinder bore 15 are closed by the valve forming body 8 and the piston 16, and a compression chamber whose volume changes according to the reciprocation of the piston 16 is formed in the cylinder bore 15. Each piston 16 is anchored to the outer peripheral portion of the swash plate 13 via a shoe 17. With this configuration, the rotational motion of the swash plate 13 accompanying the rotation of the drive shaft 11 is converted into the reciprocating linear motion of the piston 16 via the shoe 17. The piston 16, the shoe 17, the swash plate 13, the hinge mechanism 14 and the lug plate 12 constitute a crank mechanism, and the crank mechanism, the cylinder block 6 and the drive shaft 11 constitute a compression mechanism.

  A thrust rolling bearing 18 a is disposed between the lug plate 12 and the front housing 7. The thrust rolling bearing 18 a is disposed on the side that supports the rotating member (the drive shaft 11 and the lug plate 12) in the thrust direction and receives the compression reaction force generated in the compression mechanism via the lug plate 12. The drive shaft 11 is supported at its rear end portion by a thrust rolling bearing 18b disposed in the through hole 6a of the cylinder block 6, so that the thrust movement to the rear is restricted.

 A suction chamber 19 and a discharge chamber 20 are formed in the rear housing 9. The refrigerant gas in the suction chamber 19 is introduced into the cylinder bore 15 through the valve forming body 8 by the movement of each piston 16. The low-pressure refrigerant gas introduced into the cylinder bore 15 is compressed to a predetermined pressure by the movement of the piston 16 and is introduced into the discharge chamber 20 via the valve forming body 8. The suction chamber 19, the discharge chamber 20, the cylinder bore 15, and the valve forming body 8 constitute a refrigerant path.

  In the compressor 5 having the above configuration, when power is supplied from the vehicle engine to the drive shaft 11 via the power transmission mechanism, the swash plate 13 rotates together with the drive shaft 11. As the swash plate 13 rotates, each piston 16 is reciprocated at a stroke corresponding to the inclination angle of the swash plate 13, and refrigerant suction, compression, and discharge are sequentially repeated in each cylinder bore 15.

  Hereinafter, based on FIG. 2, the radial plain bearing 1 (1a and 1b) which is a slide bearing for compressors of this invention is demonstrated in detail. FIG. 2 is a perspective view and a sectional view of a radial plain bearing which is a slide bearing for a compressor according to the present invention. The radial plain bearing 1 is a multi-layered plain bearing comprising a cylindrical sintered metal base 2 and a resin layer 3 provided on the inner peripheral surface thereof. The resin layer 3 is made of a resin composition having an aromatic polyether ketone resin as a base resin, and is laminated on the inner peripheral surface of the sintered metal base 2 by a thickness of 0.1 to 0.7 mm by injection molding. Are formed integrally. The inner peripheral surface of the resin layer 3 is a sliding surface that supports the drive shaft 11 (see FIG. 1).

  The outer diameter shape of the radial plain bearing 1 is set to a shape along the through holes 6a and 7a (see FIG. 1) in the compressor. The outer peripheral surface of the radial plain bearing 1 and the inner peripheral surfaces of the through holes 6a and 7a (see FIG. 1) are set to be in close contact with each other as much as possible. Further, the inner diameter shape is a shape along the drive shaft 11 (see FIG. 1) so that the clearance with the peripheral surface of the drive shaft is the minimum necessary for rotation support in a state where the drive shaft 11 is supported. Is set to

  Conventional radial plain bearings perform machining such as cutting or grinding on the inner peripheral surface to finish the inner diameter of the sliding surface, improve roundness, and expose the bronze sintered layer. However, since the sliding bearing for a compressor of the present invention finishes the sliding surface (resin layer) by injection molding, it is not necessary to perform machining such as cutting or grinding. Further, unlike the conventional multi-layer bearing, it is not necessary to process the cutting part or bend with a lathe or a grinding machine after forming and cutting the multi-layer. As a result, the sliding surface has high dimensional accuracy while being easy to manufacture and low cost.

  Since the radial sliding bearing 1 uses the sintered metal base material 2 as the bearing base material, the molten resin of the aromatic polyetherketone resin is uneven in the surface of the sintered metal base material 2 at the time of injection molding. The resin layer 3 can be firmly adhered to the substrate 2. In injection molding, the molten resin is poured at a high speed, so that the resin tends to enter the irregularities (holes) of the porous sintered layer by shearing force while using the aromatic polyetherketone resin described later as the base resin. . Therefore, the adhesion strength between the sintered metal substrate 2 and the resin layer 3 can be ensured.

  By using a resin composition based on aromatic polyetherketone resin as the resin layer 3, the continuous use temperature is 250 ° C., heat resistance, oil / chemical resistance, creep resistance, friction wear A radial plain bearing with excellent characteristics. In addition, aromatic polyetherketone-based resins have high toughness, high mechanical properties at high temperatures, and excellent fatigue resistance and impact resistance, so when frictional force, impact, vibration, etc. are applied during use, The resin layer is difficult to peel from the sintered metal substrate. In the conventional radial sliding bearing, since the resin composition mainly composed of PTFE resin was a sliding surface, it was not possible to prevent the resin composition from peeling from the porous sintered layer at the time of abnormality. .

  Examples of the aromatic polyether ketone resin that can be used in the present invention include polyether ether ketone (PEEK) resin, polyether ketone (PEK) resin, and polyether ketone ether ketone ketone (PEKEKK) resin. Examples of commercially available PEEK resins that can be used in the present invention include: Victorex: PEEK (90P, 150P, 380P, 450P, 90G, 150G, etc.), Solvay Advanced Polymers: KetaSpire (KT-820P, KT-880P) Etc., manufactured by Daicel Degussa, Inc .: VESTAKEEEP (1000G, 2000G, 3000G, 4000G, etc.). Examples of the PEK resin include Victrex-HT manufactured by Victrex, and examples of the PEKKK resin include Victrex-ST manufactured by Victrex.

  The thickness of the resin layer 3 is set to 0.1 to 0.7 mm. The “resin layer thickness” in the present invention is the thickness of the surface portion that does not enter the sintered metal base material. In the case of a radial slide bearing, it is the thickness in the radial direction. Is the axial thickness. This thickness range is set in consideration of the insert molding surface and physical properties. When the thickness of the resin layer is less than 0.1 mm, insert molding is difficult. In addition, durability during long-term use, that is, life may be shortened. On the other hand, if the thickness of the resin layer exceeds 0.7 mm, sink marks may occur and dimensional accuracy may be reduced. In addition, heat due to friction is difficult to escape from the friction surface to the sintered metal substrate, and the friction surface temperature increases. Further, the amount of deformation due to the load increases, the true contact area on the friction surface also increases, the frictional force and the frictional heat generation increase, and the seizure resistance may decrease. In consideration of heat dissipation of the frictional heat generation to the sintered metal substrate, the thickness of the resin layer is preferably 0.2 to 0.5 mm.

  The thickness of the resin layer 3 is preferably 1/8 to 1/2 of the thickness of the sintered metal substrate 2. When the thickness of the resin layer is less than 1/8 of the thickness of the sintered metal base material, the resin layer becomes too thin relative to the base material, which may deteriorate durability during long-term use. On the other hand, if the thickness of the resin layer exceeds ½ of the thickness of the sintered metal base material, the resin layer becomes too thick relative to the base material, and heat from friction is generated from the friction surface to the sintered metal. It is difficult to escape to the base material and the friction surface temperature becomes high. Further, the amount of deformation due to the load increases, the true contact area on the friction surface also increases, the frictional force and the frictional heat generation increase, and the seizure resistance may decrease.

  Examples of the material of the sintered metal substrate 2 include iron, copper iron, copper, and stainless steel. Since the adhesion between the sintered metal substrate and the resin layer is excellent, it is preferable to employ a sintered metal whose main component is iron (which may include copper). In addition, since copper is inferior to adhesiveness (adhesiveness) with resin rather than iron, when copper is included, content of copper is 10 weight% or less. More preferably, the copper content is 5% by weight or less.

  If there is oil adhesion or oil impregnation on the sintered metal base, oil residue that decomposes and gasifies during the injection molding of the resin layer is present at the interface, so the resin layer and the sintered metal base Adhesion may be reduced. Therefore, it is preferable to use a sintered metal not impregnated with oil for the sintered metal base material before forming the resin layer. Moreover, when using oil in the process of shaping | molding or re-pressing (sizing) of a sintered metal, it is preferable to set it as the non-oil-containing sintered metal which removed oil by solvent washing etc.

  The base material made of sintered metal with iron as the main component is subjected to steam treatment to prevent oil or deposits from adhering to the sintered surface or penetrating into the sintered body during the molding or re-pressing (sizing) process. Since there is an effect to remove, variation in adhesion with the resin layer is small and stable. Moreover, antirust property can also be provided to a sintered metal substrate. The conditions for the steam treatment are not particularly limited, but a method of spraying steam heated to about 500 ° C. is common.

  The theoretical density ratio of the sintered metal substrate is preferably 0.7 to 0.9. The theoretical density ratio of the material is the ratio of the density of the sintered metal base material when the theoretical density of the material (density when the porosity is 0%) is 1. If the theoretical density ratio is less than 0.7, the strength of the sintered metal base material becomes low, and the base material may be cracked by the injection molding pressure at the time of insert molding. On the other hand, when the theoretical density ratio exceeds 0.9, the unevenness is reduced, so that the surface area and the anchor effect are lowered, and the adhesion with the resin layer is lowered. More preferably, the theoretical density ratio of the materials is 0.72 to 0.84. In this way, by setting the theoretical density ratio of the sintered metal base material to 0.7 to 0.9, it has the required denseness to ensure the bearing strength that the sintered metal base material bears, Unevenness on the surface for firmly adhering the resin layer to the sintered metal substrate can be secured. It is also possible to hold the lubricating oil on the sintered metal substrate. Furthermore, the thermal conductivity of the sintered metal substrate can be ensured.

  The resin composition for forming the resin layer may use the above aromatic polyetherketone resin as a base resin, and a fiber filler such as glass fiber, carbon fiber, aramid fiber, whisker or the like may be mixed in a dispersed state. it can. Thereby, the mechanical strength of the resin layer can be further improved. In particular, in the sliding bearing for a compressor of the present invention, since the resin layer is thin with a thickness of 0.1 to 0.7 mm, it is desirable to improve the mechanical strength.

  In addition to the fibrous filler, a solid lubricant such as PTFE resin, graphite, and molybdenum disulfide, and an inorganic filler such as calcium carbonate, calcium sulfate, mica, and talc can be blended. By blending the above-mentioned solid lubricant, it is possible to improve the seizure resistance by reducing friction even under non-lubricated conditions and even when the lubricating oil is dilute. Moreover, creep resistance can be improved by mix | blending the said inorganic filler.

  Fibrous fillers, inorganic solid lubricants (such as graphite and molybdenum disulfide), and inorganic fillers have the effect of reducing the molding shrinkage of aromatic polyether ketone resins. Therefore, there is also an effect of suppressing the internal stress of the resin layer at the time of insert molding with the sintered metal base material.

  FIG. 3 shows a radial slide bearing having a resin layer made of a resin composition containing a fibrous filler. FIG. 3 is a perspective view and a cross-sectional view of a radial plain bearing (combination of fibrous filler in a resin layer) which is a slide bearing for a compressor according to the present invention. The radial plain bearing 1 has the same configuration as that of FIG. 2 except that the fibrous filler 4 is blended in the resin layer 3.

  In forming the resin layer 3 by injection molding, by adjusting the melt flow direction of the resin composition, the fibrous filler 4 (in its length direction) is moved in the sliding direction of the slide bearing 1 (arrow in the figure). On the other hand, it is preferable to orient at an intersection angle as close to a right angle as possible at 45 degrees or more. In order to improve the mechanical strength of the resin layer, it is preferable to add a fibrous filler. However, since the end of the fiber of the fibrous filler is an edge, the end of the fiber is A certain drive shaft 11 (see FIG. 1) is easily physically damaged by wear, and the friction coefficient is difficult to stabilize. By orienting the fibrous filler (in its length direction) so as to intersect at 45 to 90 degrees with respect to the sliding direction of the sliding bearing, the edges at both ends of the fiber are 45 to 90 with respect to the sliding direction. Suitable for degrees. As a result, it is possible to reduce wear damage on the drive shaft due to the edges at both ends of the fiber and to stabilize the friction coefficient. It should be noted that the orientation of the fibrous filler is preferably closer to 90 degrees because there is less abrasion damage due to the fiber edge and the friction coefficient is stabilized. If it is 80-90 degree | times, it is especially preferable.

  The average fiber length of the fibrous filler is preferably 0.02 to 0.2 mm. If the thickness is less than 0.02 mm, a sufficient reinforcing effect cannot be obtained, and creep resistance and wear resistance may not be satisfied. When the thickness exceeds 0.2 mm, the ratio of the fiber length to the layer thickness of the resin layer becomes large, so that the thin moldability is poor. In particular, when insert molding is performed with a resin thickness of 0.2 to 0.7 mm, if the fiber length exceeds 0.2 mm, the thin moldability is impaired. In order to further improve the stability of thin-wall molding, an average fiber length of 0.02 to 0.1 mm is desirable.

  Among the fibrous fillers, it is preferable to use carbon fibers. Carbon fiber has a strong orientation in the melt flow direction of the resin when the resin layer is molded. In particular, a carbon fiber having a small diameter and a relatively short length is selected. In this case, the edges of both ends of the carbon fiber are along the sliding direction of the sliding bearing for the compressor, for example, the orientation direction is 0 to less than 45 degrees. If it exists, the drive shaft which is a counterpart material may be damaged. Therefore, when thin and short carbon fibers are used, when the resin is injection-molded, the flow direction of the molten resin is set to be perpendicular or close to the sliding direction of the sliding bearing for the compressor, and the length of the fiber Orienting the direction to be 45 to 90 degrees with respect to the sliding direction of the sliding bearing for the compressor is extremely advantageous in order to stabilize the durability and the bearing torque low.

  The carbon fibers used in the present invention may be either pitch-based or PAN-based ones classified from raw materials, but PAN-based carbon fibers having a high elastic modulus are preferred. The firing temperature is not particularly limited, but a carbonized product fired at about 1000 to 1500 ° C. is higher than that fired at a high temperature of 2000 ° C. or higher and converted to graphite (graphite). Even under PV, the drive shaft is less susceptible to wear damage, which is preferable.

  The average fiber diameter of the carbon fibers is 20 μm or less, preferably 5 to 15 μm. Thick carbon fiber exceeding this range generates extreme pressure, so the effect of improving load resistance is poor, and when the drive shaft is an aluminum alloy or non-quenched steel material, wear damage of the drive shaft increases, which is not preferable. . The carbon fiber may be a chopped fiber or a milled fiber, but a milled fiber having a fiber length of less than 1 mm is preferable in order to obtain stable thin-wall formability.

  Examples of commercially available carbon fibers that can be used in the present invention include pitch-based carbon fibers manufactured by Kureha Co., Ltd .: Kureka M-101S, M-107S, M-101F, M-201S, M-207S, M-2007S, C- 103S, C-106S, C-203S and the like. Moreover, as a similar PAN-based carbon fiber, manufactured by Toho Tenax Co., Ltd .: Besfight HTA-CMF0160-0H, HTA-CMF0040-0H, HTA-C6, HTA-C6-S, or Toray Industries, Inc .: Torayca MLD-30 , MLD-300, T008, T010, and the like.

  The resin composition forming the resin layer preferably uses the aromatic polyether ketone resin as a base resin and contains the carbon fiber and a PTFE resin as a solid lubricant as essential components.

  As the PTFE resin, any of molding powder by suspension polymerization, fine powder by emulsion polymerization, and recycled PTFE may be used. In order to stabilize the fluidity of a resin composition comprising an aromatic polyetherketone resin as a base resin, it is preferable to employ regenerated PTFE which is difficult to be fiberized by shearing during molding and hardly increases the melt viscosity.

  Regenerated PTFE is a powder that has been irradiated with a heat-treated powder (heated history added), γ-rays or electron beams. For example, a powder obtained by heat-treating molding powder or fine powder, a powder obtained by further irradiating this powder with γ-rays or an electron beam, a powder obtained by pulverizing a molding powder or a molded product of fine powder, and then a γ-ray or electron beam. There are types such as irradiated powder, molding powder or fine powder irradiated with gamma rays or electron beams. Among the regenerated PTFE, a resin composition comprising an aromatic polyether ketone resin as a base resin that does not aggregate, does not fiberize at the melting temperature of the aromatic polyether ketone resin, has an internal lubricating effect, and Since fluidity can be stably improved, it is more preferable to use PTFE resin irradiated with γ rays or electron beams.

  Examples of commercially available PTFE resins that can be used in the present invention include Kitamura Co., Ltd .: KTL-610, KTL-450, KTL-350, KTL-8N, KTL-400H, Mitsui DuPont Fluorochemical Co., Ltd .: Teflon (registered trademark). 7-J, TLP-10, Asahi Glass Co., Ltd .: Fullon G163, L150J, L169J, L170J, L172J, L173J, Daikin Industries, Ltd .: Polyflon M-15, Lubron L-5, Hoechst: Hostaflon TF9205, TF9207, etc. Can be mentioned. Further, it may be a PTFE resin modified with a perfluoroalkyl ether group, a fluoroalkyl group, or another side chain group having a fluoroalkyl group. Among the PTFE resins irradiated with γ rays or electron beams among the above, Kitamura Co., Ltd .: KTL-610, KTL-450, KTL-350, KTL-8N, KTL-8F, Asahi Glass Co., Ltd .: Fullon L169J, L170J , L172J, L173J, and the like.

  In addition, you may mix | blend a well-known resin additive with respect to a resin composition to such an extent that the effect of this invention is not inhibited. Examples of the additive include friction property improvers such as boron nitride, colorants such as carbon powder, iron oxide, and titanium oxide, and thermal conductivity improvers such as graphite and metal oxide powder.

  The resin composition for forming the resin layer preferably includes an aromatic polyether ketone resin as a base resin, 5 to 30% by volume of carbon fiber, and 1 to 30% by volume of PTFE resin as essential components. The balance excluding this essential component and other additives is an aromatic polyether ketone resin. By using this blending ratio, even under high PV conditions, the deformation and wear of the resin layer, the aggressiveness to the surface of the drive shaft which is the counterpart material are small, and the resistance to oil and the like is also high. Further, the carbon fiber is more preferably 5 to 20% by volume, and the PTFE resin is more preferably 2 to 25% by volume.

  If the blending ratio of carbon fiber exceeds 30% by volume, the melt fluidity will be significantly reduced, making it difficult to form a thin wall, and if the drive shaft that is the counterpart material is an aluminum alloy or non-quenched steel, there is a risk of wear damage There is. Moreover, when the blending ratio of the carbon fiber is less than 5% by volume, the effect of reinforcing the resin layer is poor, and sufficient creep resistance and wear resistance may not be obtained.

  If the blending ratio of the PTFE resin exceeds 30% by volume, the wear resistance and creep resistance may be lowered from the required levels. In addition, when the blending ratio of the PTFE resin is less than 1% by volume, the effect of imparting the required lubricity to the composition is poor, and sufficient sliding characteristics may not be obtained.

  The means for mixing and kneading the above raw materials is not particularly limited, and only the powder raw material is dry-mixed with a Henschel mixer, ball mixer, ribbon blender, ladyge mixer, ultra Henschel mixer, etc. Melting and kneading can be performed with a melt extruder such as an extruder to obtain molding pellets (granules). In addition, a side feed may be used for charging the filler when melt kneading with a twin screw extruder or the like. Using this molding pellet, a resin layer is injection-molded by insert molding on a sintered metal substrate. By adopting injection molding, it is excellent in precision moldability and manufacturing efficiency. Moreover, you may employ | adopt treatments, such as an annealing process, for physical property improvement.

The resin composition forming the resin layer preferably has a melt viscosity of 50 to 200 Pa · s at a resin temperature of 380 ° C. and a shear rate of 1000 s ⁻¹ . When the melt viscosity is within this range, it becomes possible to orient the precise molding and fibrous filler at a predetermined angle, and a thin insert molding of 0.1 to 0.7 mm is formed on the surface of the sintered metal substrate. It can be done smoothly. If the melt viscosity is less than the predetermined range or exceeds the predetermined range, it is not easy to reliably obtain a precise moldability and to orient the fibrous filler at a predetermined angle. By making thin insert molding possible and making post-processing after insert molding unnecessary, manufacturing becomes easy and manufacturing costs can be reduced.

In order to set the melt viscosity at a resin temperature of 380 ° C. and a shear rate of 1000 s ⁻¹ to 50 to 200 Pa · s, it is preferable to employ an aromatic polyether ketone resin having a melt viscosity of 130 Pa · s or less under these conditions. An example of such an aromatic polyether ketone resin is PEEK (90P, 90G) manufactured by Victrex.

  In order to obtain a sufficient adhesion strength against the friction force in use, the shear adhesion strength between the sintered metal substrate and the resin layer is 2 MPa or more (at a surface pressure of 10 MPa and a friction coefficient of 0.1). The safety factor is preferably 2 times or more. Furthermore, in order to raise a safety factor, 3 Mpa or more is preferable. In order to further increase the shear adhesion strength between the sintered metal substrate and the resin layer, the sintered metal surface on which the resin layer is formed may be provided with physical stoppers such as irregularities and grooves, and rotation prevention. Good.

  In the first embodiment shown in FIG. 1, the drive shaft 11 is formed by sliding the resin layer of the radial bearings 1a and 1b having excellent heat resistance, low friction, wear resistance, load resistance, creep resistance and the like. It is supported in sliding contact with the moving surface (inner peripheral surface). For this reason, wear on the sliding contact surface and deformation of the resin layer can be prevented, and low rotational torque can be stably obtained.

  In addition, a lip seal 7b is provided in a portion of the through hole 7a in front of the radial sliding bearing 1a (left side in the figure) to prevent the refrigerant gas in the housing from leaking outside through the through hole 7a. doing. Here, the radial plain bearing 1a is excellent in dimensional accuracy, and is set in a shape along this so that the clearance with the peripheral surface of the drive shaft 11 is the minimum necessary for rotation support, and The outer peripheral surface of the radial sliding bearing 1a and the inner peripheral surface of the through hole 7a are set so as to be in close contact with each other as much as possible. For this reason, it becomes easy to maintain the pressure of the space between the radial sliding bearing 1a and the lip seal 7b in the through hole 7a lower than the pressure of the crank chamber 10. With this configuration, the burden on the lip seal 7b for preventing leakage of refrigerant gas in the housing to the outside through the through hole 7a is reduced.

  Further, in the first embodiment, the radial plain bearings 1a and 1b are disposed in the crank chamber 10 that is not included in the refrigerant path in the housing. According to these radial sliding bearings 1a and 1b, even in the crank chamber 10 where the circulation amount of the refrigerant gas is relatively small and the lubricating effect by the mist-like lubricating oil mixed in the refrigerant gas is low, the radial sliding is caused by the sliding surface of the resin layer. Wear of the sliding contact portion between the slide bearings 1a and 1b and the drive shaft 11 can be suppressed. As a result, the life of the compressor can be extended. Therefore, it is particularly useful to employ the radial plain bearings 1a and 1b in the compressor of this embodiment.

  A second embodiment of the compressor using the sliding bearing for the compressor of the present invention will be described with reference to FIG. In the second embodiment, the configuration of the compressor in the first embodiment shown in FIG. 1 is replaced with a thrust rolling bearing 18a, and a thrust sliding bearing 21 that is a sliding bearing for a compressor according to the present invention is used. It has been changed to. Other configurations are the same as those of the first embodiment.

  As shown in FIG. 4, a thrust slide bearing 21 is disposed between the front housing 7 and the lug plate 12. The thrust slide bearing 21 is fixed to the lug plate 12 and is in sliding contact with an iron ring-shaped plate 24 fixed to the front housing 7. By the sliding contact between the thrust sliding bearing and the plate 24, the thrust movement of the rotating member forward (left side in the figure) is restricted.

  The thrust slide bearing 21 will be described with reference to FIG. FIG. 5 is a perspective view and a sectional view of a thrust sliding bearing which is a sliding bearing for a compressor according to the present invention. The thrust sliding bearing 21 is a multi-layered sliding composed of a ring-shaped sintered metal base material 22 and a resin layer 23 provided on a surface facing the plate 24 (see FIG. 4) of the base material. It is a bearing. The resin layer 23 is made of a resin composition having an aromatic polyetherketone resin as a base resin, and is laminated on the surface of the sintered metal base material 22 at a thickness of 0.1 to 0.7 mm by injection molding. It is formed by being provided integrally. The surface of the resin layer 23 (the side opposite to the base material) is a sliding surface that comes into sliding contact with the plate 24 (see FIG. 4). The sintered metal substrate, the resin composition, the method for forming the resin layer, and the like are the same as in the case of the first embodiment.

  In the second embodiment, a thrust sliding bearing 21 is employed as a bearing that supports the rotating member on the side that receives the compression reaction force generated in the compression mechanism through the lug plate 12 in the thrust direction. In this embodiment, the cost can be reduced as compared with the case where a rolling bearing is employed. Further, this thrust slide bearing is provided in the crank chamber 10 having a low lubrication effect that is not included in the refrigerant path, as in the case of the radial slide bearing of the first embodiment. Wear of the sliding contact portion between the bearing 21 and the plate 24 can be suppressed. As a result, the life of the compressor can be extended. Therefore, it is particularly useful to employ the thrust slide bearing 21 in the compressor of this embodiment.

  In this embodiment, a thrust sliding bearing which is a sliding bearing for a compressor according to the present invention may be employed in place of the thrust rolling bearing 18b.

  As a third embodiment of the compressor using the sliding bearing for the compressor of the present invention, an example of a double-headed piston compressor constituting a vehicle air conditioner will be described with reference to FIG. In the compressor 5 ′ of this aspect, a housing is constituted by a pair of cylinder blocks 33, a front housing 34, and a rear housing 35. Further, the drive shaft 32 and the swash plate 36 fixed to the drive shaft 32 in the crank chamber 37 constitute a rotating member. The plurality of cylinder bores 33a are formed at predetermined intervals on the same circumference between both ends of each cylinder block 33 so as to extend in parallel with the drive shaft 32. The double-headed piston 39 is inserted into and supported by each cylinder bore 33a so as to reciprocate, and a compression chamber is formed between the both end faces and the corresponding valve forming bodies 40. The shoe 38 and the swash plate 36 constitute a crank mechanism, and the crank mechanism, the cylinder block 33 (cylinder bore 33a), the piston 39, and the drive shaft 32 constitute a compression mechanism.

  The drive shaft 32 is rotatably supported at the center of the cylinder block 33 and the front housing 34 via a pair of radial slide bearings 31a and 31b, and operates on an external drive source such as a vehicle engine via a power transmission mechanism. It is connected. The radial slide bearings 31 a and 31 b are inserted into a receiving hole 33 b formed in the center of the cylinder block 33 so as to communicate with a crank chamber 37 formed inside the cylinder block 33. The radial sliding bearings 31a and 31b are the sliding bearings for the compressor of the present invention. The specific configuration is the same as that of the first embodiment except for the dimensions in the radial direction and the axial direction, and is manufactured by the same manufacturing method.

  Further, the pair of thrust rolling bearings 44 is provided between the front and rear end surfaces of the support cylindrical portion of the swash plate 36 and the central portion of each cylinder block 33 facing each other, and through the thrust rolling bearing 44. A swash plate 36 is held in a state of being sandwiched between the cylinder blocks 33.

  The insertion hole 34a of the drive shaft and the accommodation hole 33b formed in the cylinder block 33 are in communication with each other via a through hole formed in the valve forming body 40 (left side in the figure). A lip seal 34b is provided in the insertion hole 34a to prevent leakage of refrigerant gas in the housing to the outside through the insertion hole 34a. Here, the radial plain bearing 31a is set to a shape along this so that the dimensional accuracy is excellent, and the clearance with the peripheral surface of the drive shaft 32 becomes the minimum necessary for rotation support, and The outer peripheral surface of the radial sliding bearing 31a and the inner peripheral surface of the accommodation hole 33b are set so as to be in close contact with each other as much as possible. For this reason, it is easy to maintain the pressure in the space between the lip seal 34b and the radial sliding bearing 31a in the insertion hole 34a lower than the pressure in the crank chamber 37. With this configuration, the burden on the lip seal 34b for preventing leakage of refrigerant gas in the housing through the insertion hole 34a to the outside is reduced.

  In this embodiment, the crank chamber 37, the bolt insertion hole 43, the suction chamber 41, the compression chamber, the discharge chamber 42, and the like constitute a refrigerant path in the housing. Each part in the refrigerant path in the housing is lubricated by mist-like lubricating oil or the like mixed in the refrigerant gas flowing through the path. For this reason, the sliding contact portion between the radial slide bearings 31a and 31b and the drive shaft 32 disposed in the crank chamber 37 (specifically, the accommodation hole 33b) constituting the refrigerant path has a solid resin layer of the slide bearing. In addition to the lubricating action, the lubricating action by the lubricating oil works greatly. Thereby, the sliding contact portion between the drive shaft 32 and the sliding bearings 31a and 31b is well lubricated, and the life of the compressor can be extended.

  In this embodiment, a thrust sliding bearing which is a sliding bearing for a compressor according to the present invention may be employed in place of the thrust rolling bearing 44.

  As a fourth embodiment of the compressor using the sliding bearing for the compressor of the present invention, an example of a scroll type compressor constituting the vehicle air conditioner will be described with reference to FIG. In the compressor 5 ″ in this aspect, the fixed scroll 51, the center housing 52, and the motor housing 53 constitute a housing. The center housing 52 and the motor housing 53 support a shaft 54 made of iron as a rotating shaft so as to be rotatable via radial sliding bearings 55 and 56. Further, an eccentric shaft 54a is formed integrally with the shaft 54, and a balance weight 57 is supported on the shaft 54a. The shaft 54 and the balance weight 57 constitute a rotating member.

  The eccentric shaft 54 a is supported via a radial sliding bearing 59 and a bush 60 so as to be relatively rotatable so that the movable scroll 58 faces the fixed scroll 51. The radial plain bearing 59 is fitted and accommodated in a substantially cylindrical bush 60 fitted in a boss portion 58c projecting from the movable substrate 58a. The inner peripheral surface of the radial sliding bearing 59 becomes a sliding contact surface with the outer peripheral surface of the eccentric shaft 54a. A movable spiral wall 58b is formed on the movable substrate 58a of the movable scroll 58, and a fixed spiral wall 51b that meshes with the movable spiral wall 58b is formed on the fixed substrate 51a of the fixed scroll 51. A region defined by the fixed substrate 51 a, the fixed spiral wall 51 b, the movable substrate 58 a, and the movable spiral wall 58 b becomes the sealed chamber 61 whose volume decreases as the movable scroll 58 rotates. The fixed scroll 51, the movable scroll 58, the center housing 52, the bush 60, the radial sliding bearings 55 and 59, the shaft 54, the balance weight 57, and the like constitute a scroll type compression mechanism.

  A stator 62 as a stator is fixed to the inner peripheral surface of the motor housing 53, and a rotor 63 as a rotor is fixed to the outer peripheral surface of the shaft 54 at a position facing the stator 62. The stator 62 and the rotor 63 constitute an electric motor, and the rotor 63 and the shaft 54 are integrally rotated by energizing the stator 62. The center housing 52 is provided with a partition wall portion 52a, and the radial sliding bearing 55 is fitted into a through hole 52b formed at the center of the partition wall portion 52a. The inner peripheral surface of the radial sliding bearing 55 is a sliding contact surface with the outer peripheral surface of the shaft 54.

  In the shaft 54, a fluid passage 54 b that communicates the discharge chamber 64 and the motor chamber 65 and a fluid passage 54 c that communicates the motor chamber 65 and the outside of the motor housing 53 are formed. As the movable scroll 58 revolves, the refrigerant gas that has flowed into the sealed chamber 61 from the inlet of the fixed scroll 51 passes through the discharge port 58d, the discharge chamber 64, the fluid passage 54b, the motor chamber 65, and the fluid passage 54c, and passes through the motor housing. It flows out to the outside through an outlet 53 a provided in the wall portion of 53. For this reason, the discharge chamber 64, the fluid passage 54b, the motor chamber 65, and the fluid passage 54c become a high pressure region having a pressure value substantially equal to the discharge pressure. On the other hand, the outer side of the ring-shaped seal member 66 is a low pressure chamber 67 having a pressure value close to the suction pressure.

  The radial plain bearings 55, 56 and 59 are the plain bearings for the compressor of the present invention. The specific configuration is the same as that of the first embodiment except for the dimensions in the radial direction and the axial direction, and is manufactured by the same manufacturing method.

  The radial sliding bearings 55 and 59 are inserted into the through hole 52b and the bush 60, respectively, and the clearance with the peripheral surface of the shaft 54 is maintained when the shaft 54 (the bearing 59 is specifically the eccentric shaft 54a) is inserted. The shape along this is set so as to be the minimum necessary for the rotation support. The outer peripheral surface of the radial sliding bearing 55 and the inner peripheral surface of the through hole 52b are in close contact with the outer peripheral surface of the radial sliding bearing 59 and the inner peripheral surface of the bush 60 as much as possible. Is set to

  The communication between the space 68 surrounded by the outer peripheral side of the boss portion 58c and the inner peripheral side of the partition wall portion 52a and the motor chamber 65 through the clearance between the through hole 52b and the shaft 54 is substantially blocked by the radial slide bearing 55. Has been. Further, the communication between the discharge chamber 64 and the space 68 through the gap between the bush 60 and the eccentric shaft 54 a is substantially blocked by a radial sliding bearing 59. That is, the radial plain bearings 55 and 59 are provided so as to pressure-isolate the internal space of the housing.

  The space 68 is formed by adjusting the pressure of the regulating valve or leaking refrigerant gas from the high pressure region (the motor chamber 65 or the discharge chamber 64) through a slight gap between the radial slide bearings 55 and 59 and the shaft 54. The intermediate pressure is maintained at a lower pressure than that of the low pressure chamber 67. By providing a region (space 68) whose pressure is lower than that of the high pressure region on the back surface of the movable scroll 58, a load applied to the movable scroll 58 due to the pressure applied to the back surface of the movable scroll 58 is reduced. Therefore, smooth revolution of the movable scroll 58 is obtained, and mechanical loss of the movable scroll 58 is reduced.

  Since the radial slide bearings 55 and 59 are excellent in wear resistance as described above, the wear of the sliding contact portion with the shaft 54 can be reduced, and the reduction of the pressure isolation effect due to the widening of the gap between the two due to this wear is suppressed. it can. As described above, the radial plain bearings 55 and 59 can exhibit good sealing performance with the shaft 54, and it is easy to maintain the effect high. For this reason, the discharge chamber 64 and the space 68 can be effectively separated from the motor chamber 65 and the space 68 by pressure without providing a special seal member.

  The first to fourth embodiments have been described above, but the embodiment of the present invention is not limited to this.

[Examples 1 to 20, Comparative Examples 1 to 4]
Table 1 shows the specifications of the sintered metal base materials used in the examples and comparative examples. The cylindrical base material ((phi) 30 * (phi) 35 * 20 (mm)) of the base material A-the base material I and the base material K was prepared for the Example and the comparative example.

Moreover, the raw material of the resin layer used for the Example and the comparative example is shown below.
The melt viscosity of the aromatic polyether ketone resin is a measured value at a Capillograph manufactured by Toyo Seiki Co., Ltd., φ1 × 10 mm capillary, a resin temperature of 380 ° C., and a shear rate of 1000 s ⁻¹ .
(1) Aromatic polyether ketone resin [PEK-1]: PEEK 90P (melt viscosity: 105 Pa · s) manufactured by Victrex
(2) Aromatic polyetherketone resin [PEK-2]: PEEK 150P (melt viscosity 145 Pa · s) manufactured by Victrex
(3) PAN-based carbon fiber [CF-1]: Torayca MLD-30 manufactured by Toray Industries, Inc. (average fiber length 0.03 mm, average fiber diameter 7 μm)
(4) PAN-based carbon fiber [CF-2]: Besfight HTA-CMF0160-0H manufactured by Toho Tenax Co., Ltd. (fiber length 0.16 mm, fiber diameter 7 μm)
(5) Pitch-based carbon fiber [CF-3]: Kureha Kureka M-101S (average fiber length 0.1 / 2 mm, average fiber diameter 14.5 μm)
(6) Pitch-based carbon fiber [CF-4]: Kureha Kureka M-107S (average fiber length 0.7 mm, average fiber diameter 14.5 μm)
(7) Calcium carbonate powder [CaCO ₃ ]: NA600 (average particle size: 3 μm) manufactured by Nittsu Kogyo Co., Ltd.
(8) Graphite [GRP]: TIMEX KS6 (average particle size 6 μm) manufactured by Timcal Japan
(9) Tetrafluoroethylene resin [PTFE]: KTL-610 (regenerated PTFE) manufactured by Kitamura Co., Ltd.

  The raw materials for the resin layer were dry blended using a Henschel dry mixer at the blending ratio (volume%) shown in Table 2, and melt-kneaded using a twin screw extruder to produce pellets for injection molding.

  In Examples and Comparative Examples, this pellet is used, and a resin layer is formed on the inner diameter of a cylindrical base material by insert molding (resin temperature 380 ° C. to 400 ° C., mold temperature 180 ° C.), as shown in FIG. A cylindrical slide bearing (φ30 × φ35 × 20 (mm)) supporting a radial load was manufactured. The sintered dimension of the cylindrical base material is φ30 × φ35 × 20 (mm). In order to form a resin layer on the cylindrical substrate with a predetermined thickness, the inner surface of the cylindrical base material is turned and insert-molded. I did it. At the time of insert molding, nine pin gates were provided on the bearing end face so that the melt flow direction of the resin layer was perpendicular to the direction of motion of the sliding bearing.

  In Examples 1 to 9 and Comparative Example 1, pellets of the resin composition a (Table 2) are used for the inner diameter (φ31 mm) of the cylindrical base material composed of the base material A to the base material I and the base material K (Table 1). A cylindrical sliding bearing with a resin layer thickness of 0.5 mm was manufactured by insert molding. In Examples 10 to 20 and Comparative Example 2, the resin layer thickness was determined by using pellets of resin composition a to resin composition h (Table 2) on the inner diameter of a cylindrical substrate made of the substrate E (Table 1). A cylindrical sliding bearing (φ30 × φ35 × 20 (mm)) of 0.2 to 1.0 mm was manufactured by insert molding.

  Comparative Example 3 is a plain bearing made of a single resin injection molded into a shape of φ30 × φ35 × 20 (mm) using the resin composition a (Table 2). Comparative Example 4 is a three-layer slide bearing (φ30 × φ35 × 20 mm, resin layer 0) in which a porous sintered layer (Cu + Sn) with a back metal (SPCC) is impregnated with a PTFE resin composition (10% by volume of carbon fiber). 0.05 mm).

(1) Shear adhesion strength test Using the sliding bearings of Examples 1 to 9 and Comparative Example 1, a shear adhesion strength test was performed. In this shear adhesion strength test, a cylindrical substrate is fixed, an axial shear force is applied to the resin layer, a load at which the resin layer peels from the sintered metal substrate is measured, and the resin layer Table 3 shows the value obtained by dividing the apparent bonding area of the sintered metal substrate and the shear adhesion strength. In addition, 30 slide bearings were insert-molded, and the presence or absence of cracks in the cylindrical base material due to the molding pressure was confirmed.

  As shown in Table 3, Examples 1 to 9 were free from cracks in the sintered metal substrate during insert molding, and had a shear adhesion strength of 1.5 MPa or more. In particular, in Examples 1 to 8 using the base materials A to H in which the density of the sintered metal base material is 0.7 to 0.9 of the theoretical density ratio of the materials, the shear adhesion strength was 2 MPa or more. . On the other hand, in the steel machined product, the shear adhesion strength was very low (Comparative Example 1).

(2) Seizure resistance test Using the slide bearings of Examples 10 to 20 and Comparative Examples 2 to 4, seizure resistance tests were performed with a radial in-oil tester. After running-in for 30 minutes under the oil supply conditions shown in Table 4, the time from oil supply stop / oil discharge to seizure was measured. Seizure is the time required for the temperature of the outer diameter of the slide bearing to rise by 20 ° C. or the torque to double, and is shown in Tables 5 and 6.

(3) Wear test About the same cylindrical sliding bearing as the seizure resistance test, the wear amount after operating for 30 hours under the oil supply conditions in Table 4 was measured using a radial in-oil tester.

(4) Melt viscosity The melt viscosity at Toyo Seiki Co., Ltd. Capiragraph, φ1 × 10 (mm) capillary, resin temperature 380 ° C., shear rate 1000 s ⁻¹ was measured and shown in Tables 5 and 6.

  In Examples 10 to 20, the seizure time was 30 minutes or more, the wear amount was 10 μm or less, and the seizure resistance and the wear resistance were excellent.

  In Comparative Example 2 in which the thickness of the resin layer exceeded 0.7 mm, the seizure time was less than 1 minute, and the wear amount was very large. Since Comparative Example 3 was abnormally worn within 30 minutes, the seizure resistance test could not be performed. The sliding bearing of Comparative Example 4 seized immediately after a seizure time of less than 1 minute, and the amount of wear was large.

  The plain bearing for a compressor according to the present invention is easy to manufacture, has high dimensional accuracy, is excellent in heat resistance, low friction, wear resistance, load resistance, creep resistance, and low rotational torque. Therefore, in a compressor for a room air conditioner or a car air conditioner, it can be suitably used as a sliding bearing that rotatably supports a rotating member for driving the compression mechanism.

1, 1a, 1b Radial plain bearing (slider bearing for compressor)
2, 22 Sintered metal base material 3, 23 Resin layer 4 Fibrous filler 5, 5 ', 5''Compressor 6 Cylinder block 7 Front housing 8 Valve forming body 9 Rear housing 10 Crank chamber 11 Drive shaft 12 Lug Plate 13 Swash plate 14 Hinge mechanism 15 Cylinder bore 16 Piston 17 Shoe 18a, 18b Thrust rolling bearing 19 Suction chamber 20 Discharge chamber 21 Thrust sliding bearing (sliding bearing for compressor)
24 Plate 31a, 31b Radial plain bearing (slider bearing for compressor)
32 Drive shaft 33 Cylinder block 33a Cylinder bore 33b Accommodating hole 34 Front housing 34a Insertion hole 34b Lip seal 35 Rear housing 36 Swash plate 37 Crank chamber 38 Shoe 39 Piston 40 Valve forming body 41 Suction chamber 42 Discharge chamber 43 Bolt insertion hole 44 Thrust rolling Bearing 51 Fixed scroll 51a Fixed substrate 51b Fixed spiral wall 52 Center housing 52a Partition wall 52b Through hole 53 Motor housing 53a Outlet 54 Shaft 54a Eccentric shaft 54b, 54c Fluid passage 55, 56, 59 Radial sliding bearing (sliding bearing for compressor)
57 Balance weight 58 Movable scroll 58a Movable substrate 58b Movable spiral wall 58c Boss portion 58d Discharge port 60 Bush 61 Sealed chamber 62 Stator 63 Rotor 64 Discharge chamber 65 Motor chamber 66 Seal member 67 Low pressure chamber 68 Space

Claims (14)

A sliding bearing for a compressor that rotatably supports a rotating member for driving a compression mechanism of the compressor,
The sliding bearing has a sliding surface of a resin layer made of a resin composition based on an aromatic polyether ketone-based resin on a sintered metal base,
The resin composition includes a fibrous filler, and the fibrous filler in the resin layer is oriented so that the length direction of the fiber intersects 45 to 90 degrees with respect to the sliding direction of the sliding bearing. And
The slide bearing for a compressor, wherein the resin layer is an injection-molded layer integrally provided with a thickness of 0.1 to 0.7 mm on the surface of the sintered metal base material.   The sliding bearing for a compressor according to claim 1, wherein the thickness of the resin layer is 1/8 to 1/2 of the thickness of the sintered metal substrate. The sliding bearing for a compressor according to claim 1 or 2, wherein a theoretical density ratio of the sintered metal base material is 0.7 to 0.9. The sliding bearing for a compressor according to any one of claims 1 to 3 , wherein the sintered metal substrate is made of a sintered metal containing iron as a main component. The average fiber length of the fibrous filler is, claim 1 to any one slide bearing for a compressor according to claim 4, characterized in that a 0.02 to 0.2 mm. The fibrous filler is, claim 1 to any one slide bearing for a compressor according to claim 5, characterized in that a carbon fiber. The slide bearing for a compressor according to claim 6 , wherein the carbon fiber is a PAN-based carbon fiber. The said resin composition contains 5-30 volume% of said carbon fibers and 1-30 volume% of polytetrafluoroethylene resin with respect to this resin composition whole, The Claim 6 or Claim 7 characterized by the above-mentioned. Sliding bearing for compressor. The compression according to any one of claims 1 to 8 , wherein the resin composition is a resin composition having a melt temperature of 50 to 200 Pa · s at a resin temperature of 380 ° C and a shear rate of 1000 s ^-1 . Sliding bearing for machine. The sliding bearing for a compressor according to any one of claims 1 to 9 , wherein the sliding bearing is a bearing that supports the rotating member in a radial direction. The sliding bearing for a compressor according to claim 10 , wherein the sliding bearing is disposed so as to pressure-isolate an internal space in the housing of the compression mechanism. The sliding bearing for a compressor according to any one of claims 1 to 11 , wherein the sliding bearing is a bearing that supports the rotating member in a thrust direction. The sliding bearing for a compressor according to claim 12 , wherein the sliding bearing is disposed on a side that receives a compression reaction force generated in the compression mechanism via the rotating member. 14. A compressor comprising a sliding bearing that rotatably supports a rotating member for driving a compression mechanism, wherein the sliding bearing is a sliding bearing for a compressor according to any one of claims 1 to 13. The compressor characterized by being.

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