KR100441354B1 - Inclination plate type compressor - Google Patents

Abstract

Foreign matters are not adversely affected such as deteriorating the sliding contact property of the sliding contact film on the inclined plate.

The shoes 18A and 18B are provided with a flat surface portion 34 in contact with the inclined plate 15 and a sphere 35. The flat surface portion 34 is composed of a spherical convex surface portion 341 having a very large radius of curvature and an annular main chamfer portion 342. The circumferential chamfer 342 is formed around the main chamfer 342. The average of the inclination angle θ1 of the main chamfer 342 with respect to the surface H in contact with the center P of the flat surface portion 34 is a gentle inclination angle less than or equal to a predetermined angle, and the plane H and the main chamfer The maximum spacing β of 342 is smaller than the film thickness D of the sliding contact films 32 and 33.

Description

Inclined Plate Compressor {INCLINATION PLATE TYPE COMPRESSOR}

The present invention includes a shoe having a flat surface portion in contact with an inclined plate which is integrally rotated with a rotating shaft, and a spherical surface portion fitted with a fitting recess of the piston, between the inclined plate and the piston, and the rotational force of the inclined plate is measured. The present invention relates to an inclined plate type compressor provided with a sliding contact membrane in a sliding contact area with respect to the shoe of the inclined plate by transferring the piston through a shoe to reciprocate the piston.

As disclosed in Japanese Unexamined Patent Publication No. 61-1636 and Japanese Unexamined Patent Application Publication No. Hei 11-193780, the piston in the inclined plate compressor is reciprocated by the rotational operation of the inclined plate which rotates integrally with the rotating shaft. . Shoe is interposed between the terminal surface before and behind the inclination plate, and the piston, and the rotational force of the inclination plate is transmitted to the piston through the shoe. Since the shoe made of iron material is in sliding contact with the rotating inclined plate, the sliding contact portion between the shoe and the inclined plate may be worn, or a scissor may occur between the shoe and the inclined plate. Therefore, it is necessary to improve the sliding motion of the inclined plate with respect to the shoe.

In the compressor in Japanese Patent Application Laid-Open No. 61-1636, the plane of the hemispherical shoe is made a convex curved surface having a very large radius of curvature, and first and second chamfers are provided on the outer circumferential edge of the convex curved surface. The inclination angle of the second chamfer portion inside the first chamfer portion is smaller than the inclination angle of the first chamfer portion. The first and second chamfers function to draw oil on the end face of the inclined plate in sliding contact with the shoe between the shoe and the end face of the inclined plate. The configuration that draws a lot of oil between the shoe and the end face of the inclined plate improves the sliding motion of the inclined plate relative to the shoe.

In order to further improve the sliding motion of the inclined plate with respect to the shoe, the inclined plate in Japanese Patent Laid-Open No. 11-19370 is provided with a sliding contact film excellent in sliding contact with the terminal surfaces before and after the inclined plate in sliding contact with the shoe.

Since there are foreign substances (grinding debris, abrasive powder, etc. at the time of grinding parts) inside the compressor and the external refrigerant circuit, measures to arrange the filter on the passage of the refrigerant gas are taken, as in JP-A-6-336978. In order to avoid clogging in the filter, a filter capable of filtering only foreign substances of a certain size or more may be used, and foreign matter having passed through such a filter may enter between the inclined plate and the shoe. In the installed compressor, the sliding contact membrane may be damaged depending on the size of the foreign matter between the inclined plate and the shoe, and if the sliding contact membrane is damaged, the sliding contactability of the sliding contact membrane is reduced.

An object of the present invention is to prevent foreign matters from adversely affecting the sliding contactability of the sliding contact membrane.

BRIEF DESCRIPTION OF THE DRAWINGS The 1st Embodiment is shown, (a) is a side sectional view of the whole compressor, (b) is an enlarged main sectional side view.

Figure 2 is an enlarged side view incorporating the main portion enlarged side cross-sectional view.

3 is a similar profile of the shoe.

4 is an enlarged sectional side view of a main portion showing the second embodiment;

Fig. 5 is an enlarged sectional side view of a main portion showing the third embodiment;

6 is an enlarged sectional side view of a main portion showing the fourth embodiment;

(Explanation of symbols for the main parts of the drawing)

13. Rotating shaft 15. Inclined plate

152,153 Terminal surface for sliding contact area

17.Piston 172,173. Fitting recess

18A, 18B, 18C, 18D, 18E. Shoe 32,33. Sliding contact membrane

321,331. Metal layer 322,332; Resin layer

34. Flat surface portion 341. Convex surface portion

342. Main moss part 35. Spherical part

36. Parenting H. Plane

P. Center of Flat Surface

Therefore, the present invention interposes the inclined plate between the inclined plate and the piston with a shoe having a flat surface portion in contact with the inclined plate which is integrally rotated with the rotating shaft, and a spherical portion fitted with the fitting recess of the piston. An inclination plate type compressor having a sliding contact membrane provided in a sliding contact area of the inclined plate to the piston by transmitting a rotational force to the piston through the shoe, and in the invention of claim 1, The main chamfering portion is provided on the outer circumferential side of the flat surface portion, and the inclination angle of the main chamfering portion with respect to the plane in contact with the center of the flat surface portion is a gentle inclination angle of less than a predetermined angle, and the maximum distance between the main chamfering portion and the plane. Was set to the film thickness of the sliding contact film.

The main chamfer part whose inclination-angle with respect to the plane which contact | connects the center of a flat surface part becomes below a predetermined angle has the space | interval with the said plane below the film thickness of a sliding contact film. If foreign matter of a diameter smaller than the film thickness of the sliding contact film enters between the main chamfer portion and the inclined plate, the foreign matter is completely buried in the sliding contact film, and therefore, it is not electrically driven between the shoe and the inclined plate. When foreign matter of a diameter larger than the film thickness of the sliding contact membrane enters between the main chamfer portion and the inclined plate, the foreign matter may be driven in a state sandwiched between the shoe and the inclined plate, and the sliding contact membrane may be damaged. In this way, damage to the sliding contact film is a foreign matter of a diameter larger than the film thickness of the sliding contact film, but foreign matters of a diameter larger than the film thickness of the sliding contact film are difficult to enter between the main chamfer portion and the inclined plate.

In the invention of claim 2, the parent cutting part is provided so as to surround the main cutting part and to be connected to the main cutting part, and the inclination angle of the parent cutting part is made larger than the predetermined angle.

The parent scraping portion whose inclination angle with respect to the plane in contact with the center of the flat surface portion is larger than the predetermined angle is effective for oil inflow between the flat surface portion and the inclined plate. In addition, since the inclination angle is large, foreign matter in contact with the parent scraping portion is blocked there and does not enter the shoe.

In the invention of claim 3, the flat surface portion is constituted by a convex surface portion whose inclination angle with respect to the plane is less than or equal to the inclination angle of the main chamfer portion, and the main chamfer portion.

The convex surface portion contributes to oil inflow between the inclined plate and the central portion of the flat surface portion. In invention of Claim 4, the said predetermined angle was 20 degrees in any one of Claims 1-3.

When the inclination angle of the main chamfer portion exceeds 20 °, there is almost no risk of damaging the sliding contact membrane even if foreign matter larger than the film thickness of the sliding contact membrane flows between the main chamfer portion and the inclined plate.

In the invention of claim 5, the sliding contact film is composed of a metal layer formed on the surface of the sliding contact region of the inclined plate, and a resin layer containing a solid lubricant formed on the metal layer.

The resin layer is particularly effective in a lubricating oil-free state, but is easily damaged by foreign matter. It is difficult for foreign matter of diameter larger than the film thickness of the sliding contact membrane to flow between the main chamfer portion and the resin layer on the inclined plate.

In the sixth aspect of the present invention, in the fifth aspect, the inclined plate is made of iron, and the metal layer is made of aluminum or copper.

Aluminum or copper-based materials are most suitable as metal layers.

(Example)

EMBODIMENT OF THE INVENTION Hereinafter, the 1st Example which actualized this invention is described based on FIG.

Figure 1 (a) shows the internal structure of a variable displacement compressor. The rotating shaft 13 is supported by the front housing 12 and the cylinder block 11 forming the control pressure chamber 121. The rotary shaft 13 obtains a rotary driving force from an external drive source (for example, a vehicle engine). The rotary support 14 is fixed to the rotary shaft 13, and the inclined plate 15 is supported to be slidable and inclined in the axial direction of the rotary shaft 13. The support plate 151 is integrally formed on the inclined plate 15 made of iron-based material, and the guide pin 16 is fixed to the support plate 151. The guide pin 16 is slidably fitted into the guide hole 41 formed in the rotary support 14. The inclined plate 15 is capable of tilting in the axial direction of the rotary shaft 13 by linkage between the guide hole 141 and the guide pin 16, and is integrally rotatable with the rotary shaft 13. The inclined motion of the inclined plate 15 is guided by the slide guide relationship between the guide hole 141 and the guide pin 16 and the slide support action of the rotary shaft 13.

The inclination angle of the inclined plate 15 changes based on the pressure control in the control pressure chamber 121. When the pressure in the control pressure chamber 121 increases, the inclination angle of the inclination plate 15 decreases, and when the pressure in the control pressure chamber 121 decreases, the inclination angle of the inclination plate 15 increases. The refrigerant in the control pressure chamber 121 flows out into the suction chamber 121 in the rear housing 19 through a pressure discharge passage (not shown), and the refrigerant in the discharge chamber 192 in the rear housing 19 is not shown. It is possible to supply to the control pressure chamber 121 through the pressure supply passage. The capacity control valve 25 is interposed on the pressure supply passage, and the refrigerant flow rate supplied from the discharge chamber 192 to the control pressure chamber 121 is controlled by the capacity control valve 25. If the refrigerant flow rate supplied from the discharge chamber 192 to the control pressure chamber 121 increases, the pressure in the control pressure chamber 121 increases, and if the refrigerant flow rate supplied from the discharge chamber 192 to the control pressure chamber 121 decreases, the control is performed. The pressure in the pressure chamber 121 decreases. That is, the inclination angle of the inclination plate 15 is controlled by the capacity control valve 25.

The maximum inclination angle of the inclined plate 15 is defined by the abutting contact of the inclined plate 15 and the rotary support 14. The minimum inclination angle of the inclined plate 15 is defined by the abutting contact between the circlip 24 on the rotating shaft 13 and the inclined plate 15.

In the cylinder block 11, a plurality of cylinder bores 11 (only two are shown in Fig. 1A) are arranged around the rotation shaft 13. Each cylinder bore 111 has a piston 17 housed therein. A holding part 171 is formed in the piston 17, and a pair of spherical fitting recesses 172 and 173 are formed in the holding part 171. As shown in FIG. 1B, the hemispherical shoe 18A is detachably held in the fitting recess 172, and the hemispherical shoe 18B is detachably held in the fitting recess 173. Maintained.

The rotational movement of the inclined plate 15 which is integrally rotated with the rotary shaft 13 is converted into forward and backward reciprocating motion of the piston 17 through the hemispherical shoes 18A and 18B, and the piston 17 is a cylinder bore 111. ) I move forward and backward. The shoe 18A made of iron material is in sliding contact with the sliding contact surface 30 on one side of the inclined plate 15, and the shoe 18B made of iron material is in sliding contact with the other sliding contact surface 31 of the inclined plate 15. .

The refrigerant in the suction chamber 191 moves from the suction port 201 on the valve plate 20 to the valve-forming plate 21 by the reciprocating motion of the piston 17 (moving from right to left in FIG. 1A). The suction valve 211 on the ()) is pushed out and retracted to flow into the cylinder bore 111. The refrigerant introduced into the cylinder bore 111 is formed from the valve forming plate from the discharge port 202 on the valve plate 20 by the reciprocating motion of the piston 17 (moving from left to right in FIG. 1 (a)). The discharge valve 221 on the 22 is pushed out and discharged to the discharge chamber 192. The discharge valve 221 is in contact with the retainer 231 on the retainer forming plate 23 to restrict the opening degree.

The discharge chamber 192 and the suction chamber 191 are connected through an external refrigerant circuit 26. The refrigerant flowing out of the discharge chamber 192 into the external refrigerant circuit 26 is returned to the suction chamber 191 via the condenser 27, the expansion valve 28, and the evaporator 29.

As shown in Figs. 1A and 1B, sliding contact films 32 and 33 are formed on the terminal surfaces 152 and 153 of the inclined plate 15 facing the cylinder block 11, respectively. The sliding contact films 32 and 33 are formed on the metal layers 321 and 331 formed on the terminal surfaces 152 and 153 serving as the sliding contact regions, and the resin layers 322 formed on the metal layers 321 and 331. It is a two-layer structure with (332). The surfaces of the resin layers 322 and 332 become sliding contact surfaces 30 and 31.

The metal layers 321 and 331 formed on the terminal surfaces 152 and 153 which are the original ground surfaces of the inclined plate 15 are made of an aluminum-based material whose main material is aluminum containing silicon. The resin layers 322 and 332 formed on the metal layers 321 and 331 are made of a material decomposed into a resin such as polyamideimide of a solid lubricant (for example, molybdenum dihydrate or graphite). That is, the sliding contact films 32 and 33 are made of a material which is much softer than that of the inclined plate 15. The thickness of the metal layers 321 and 331 is about 60-70 micrometers, and the thickness of the resin layers 322 and 332 is about 10-20 micrometers. The thickness D of the sliding contact films 32 and 33 is about 70 to 90 µm.

As shown in FIG. 2, the hemispherical shoes 18A and 18B have a flat surface portion 34 in contact with the inclined plate 15 and a spherical portion fitted with the fitting recesses 172 and 173 of the piston 17. 35 is provided. The flat surface portion 34 is composed of a spherical convex surface portion 341 having a very large radius of curvature, and an annular main chamfer portion 342 smoothly connected to the peripheral edge of the convex surface portion 341. Around the main chamfer 342, an annular parent chamfer 36 is formed to smoothly connect to the peripheral edge of the main chamfer 342.

3 shows a similar profile in which the profiles of the flat surface portion 34 and the parent scraping portion 36 are extended in a direction orthogonal to the flat surface portion 34. The point P represents the center of the flat surface portion 34, and H represents the plane in contact with the center P of the flat surface portion 34. The average of the inclination angle θ1 of the main chamfer 342 with respect to the plane H is a few degrees, and the average of the inclination angle θ2 of the parent chamfer 36 with respect to the plane H is about 40 °. Inclination angle (theta) 1 (theta) 2 is the inclination with respect to the plane H of the line which contact | connects the main chamfer part 342 and the parent chamfer part 36 in the radial direction of the shoes 18A and 18B. The maximum distance α between the plane H and the convex surface portion 341 is about several μm, and the maximum distance β between the plane H and the main chamfer 342 is about 10 μm. The maximum spacing γ between the plane H and the parent scraping portion 36 is larger than the film thickness D of the sliding contact films 32 and 33.

As the inclined plate 15 rotates, the lubricant on the sliding contact surfaces 30 and 31 of the inclined plate 15 passed by the shoes 18A and 18B passes through the parent scraping portion 36 and the inclined plate 15. Between the main chamfering portion 342 and the sliding contact surfaces 30 and 31 of the inclined plate 15 and the sliding contact surfaces of the convex surface 341 and the inclined plate 15 between the sliding contact surfaces 30 and 31. It is introduced between 30 and 31.

In the first embodiment, the following effects are obtained.

(1-1) The average of the inclination angle θ1 of the main chamfer 342 with respect to the plane H in contact with the center P of the flat surface portion 34 is as small as a few degrees, and such a small inclination angle θ1 is obtained. If foreign matter is caught between the main chamfer 342 and the slant plate 15 now, the sliding contact films 32 and 33 are damaged. However, the maximum distance β between the main chamfer portion 342 and the sliding contact surfaces 30 and 31 is about 10 μm, and is larger than the film thickness D of the sliding contact films 32 and 33 (about 70 to 90 μm). The foreign matter having a large diameter does not flow between the main chamfer 342 and the sliding contact surfaces 30 and 31.

On the other hand, foreign matter having a diameter larger than the film thickness D of the sliding contact films 32 and 33 flows in between the parent scraping portion 36 and the sliding contact surfaces 30 and 31. However, in the configuration in which the average of the inclination angle θ2 of the parent scraping part 36 with respect to the plane H is set to about 40 °, foreign matter does not get caught between the parent scraping part 36 and the sliding contact surfaces 30 and 31. .

Therefore, foreign matter larger than the film thickness D, which tends to damage the sliding contact films 32, 33, does not get caught between the current of the inclined plate 15 and the shoes 18A, 18B, and slips by foreign matter. Damage to the contact films 32 and 33 is prevented.

The foreign matter of aluminum and the foreign matter of iron were put into the control pressure chamber 121, and the test which operated the compressor for 1 hour and investigated the damage of the resin layers 322 and 332 was performed. The total weight of the foreign matter was 12 mg, the weight ratio of the foreign matter of aluminum to the foreign matter of iron was 2: 1, and the maximum diameter of the foreign matter was 100 μm. In this test, it was confirmed that the wear of the resin layers 322 and 332 did not occur.

(1-2) The parent scraping portion 36 having a large inclination angle θ2 is a flat surface portion 34 for lubricating oil on the sliding contact surfaces 30 and 31 of the inclined plate 15 passed by the shoes 18A and 18B. And the sliding contact surfaces 30 and 31 of the inclined plate 15 are effective.

(1-3) The average of the inclination angle θ2 of the parent tearing section 36 is about 40 °, but if the inclination angle θ2 exceeds 20 °, the parent peeling section 36 and the sliding contact surface 30 (31) ), Even if a foreign material of a diameter larger than the film thickness (D) of the sliding contact film (32) (33) enters between the parent scraping portion (36) and the sliding contact surface (30) (31). There is no work. That is, even if a foreign material having a diameter larger than the film thickness D enters between the chamfer portion having an inclination angle of more than 20 ° and the sliding contact surfaces 30 and 31 of the inclined plate 15, the sliding contact films 32 and 33 are damaged. Very little to wear. Therefore, when the inclination angle θ2 of the parent chamfer 36 exceeds 20 °, the main chamfer 342 and the sliding contact surface (only when the inclination angle θ1 of the main chamfer 342 is 20 ° or less). 30) If the maximum distance β between the 31 and 31 is less than or equal to the film thickness D of the sliding contact films 32 and 33, the sliding contact films 32 and 33 are damaged by foreign matter. none.

(1-4) The sliding contact between dissimilar materials is less likely to occur than the sliding contact between the same materials. The aluminum-based material, which is a kind of material different from the inclined plate 15 made of iron-based material, is most suitable as the metal layers 321 and 331 constituting the sliding contact films 32 and 33 in terms of preventing scissoring.

(1-5) It is the sliding contact film 32 that draws lubricant between the sliding contact surfaces 30 and 31 of the inclined plate 15 and the center of the flat surface portion 34 of the shoes 18A and 18B. It is important to extend the life of the (33). The convex surface portion 341 plays a large role in attracting lubricant between the sliding contact surfaces 30 and 31 of the inclined plate 15 and the central portion of the flat surface portion 34 of the shoes 18A and 18B.

(1-6) The parent scraping section 36 prevents acute angles such as contacting the inclined plate 15 to be the shoes 18A and 18B. In other words, the parent scraping portion 36 contributes to the prevention of angular friction between the inclined plate 15 and the shoes 18A and 18B.

Next, a second embodiment of FIG. 4 is shown. The same code | symbol is attached | subjected to the same structural part as 1st Embodiment.

The convex surface part 341 and the main chamfering part 342C of the shoe 18C are smoothly connected, and the main chamfering part 342C and the parental ripping part 36C are connected smoothly. The average of the inclination angle θ1 of the main chamfer 342C with respect to the plane H of the shoe 18C is set to 10 degrees, and the average of the inclination angle θ2 of the parent chamfer 36C with respect to the plane H. Is the same as in the case of the first embodiment. The maximum spacing β of the main chamfer 342C with respect to the plane H is about 70 to 80 m. The film thickness D of the sliding contact films 32 and 33 is the same as in the first embodiment.

Also in 2nd Embodiment, the same effect as the case of 1st Embodiment is acquired. Next, the third embodiment of FIG. 5 is shown. The same code | symbol is attached | subjected to the same structural part as 1st Embodiment.

The convex surface part 341 and the main chamfer 342D of the shoe 18D are smoothly connected, and the main chamfer 342D and the parent chamfer 36D are smoothly connected. The mean of the inclination angle θ1 of the main chamfer 342D with respect to the plane H of the shoe 18D is about 10 °, and the mean of the inclination angle θ2 of the parent peeping portion 36D with respect to the plane H is 60. It is about °. The maximum spacing β of the main chamfer 342D with respect to the plane H is about 70 to 80 m. The film thickness D of the sliding contact films 32 and 33 is the same as in the first embodiment.

Also in 3rd Embodiment, the same effect as the case of 1st Embodiment is acquired. Next, the fourth embodiment of FIG. 6 is shown. The same code | symbol is attached | subjected to the same structural part as 1st Embodiment.

The convex surface part 341 of the shoe 18E and the parental cutting part 342E are connected smoothly, and the main cutting part 342E and the parental cutting part 36E are connected smoothly. The main chamfer 342E is made up of a convex chamfer 342E1 and a concave chamfer 342E2 surrounding the convex chamfer 342E1. The convex chamfer 342E1 and the concave chamfer 342E2 are connected smoothly. The average of the inclination angle (theta) 1 of the main chamfer 342E with respect to the plane H of the shoe 18E is 10 degrees, and the average of the inclination angle (theta) 2 of the parent ripping part 36E with respect to the plane H. Is about 40 °. The maximum spacing β of the main chamfer 342D with respect to the plane H is about 70 to 80 m. The film thickness D of the sliding contact films 32 and 33 is the same as in the first embodiment.

Also in 4th Embodiment, the same effect as the case of 1st Embodiment is acquired. In the present invention, the following embodiments are also possible.

(1) The present invention is applied to a compressor using an inclined plate having only a sliding contact film made of resin containing a solid lubricant.

(2) The present invention is applied to a compressor using an inclined plate provided with only a metal sliding contact film.

(3) In 2nd-4th embodiment, a parent cutting part is removed and a main cutting part is directly connected to the spherical part of a shoe.

The invention other than the claims described in the above embodiments will be described as follows.

(1) The inclined plate compressor according to any one of claims 1 to 6, wherein the spacing between the main chamfer portion and the plane gradually increases as it goes outward from the center of the flat surface portion.

(2) The inclined plate compressor according to any one of claims 1 to 6, wherein the flat surface portion is a convex curved surface having the center of the flat surface portion as a vertex.

(3) The inclined plate compressor of claim 5, wherein the metal layer is made of a metal softer than that of the inclined plate.

As described above, in the present invention, in the present invention, the main chamfering portion is provided on the outer circumferential side of the flat surface portion of the shoe, and the inclination angle of the main chamfering portion with respect to the plane in contact with the center of the flat surface portion is a gentle inclination angle of less than a predetermined angle. Since the maximum spacing between the main chamfer portion and the plane is equal to or less than the film thickness of the sliding contact film, it is possible to achieve an excellent effect of preventing foreign matter from adversely affecting the sliding contact property of the sliding contact film.

Claims (6)

A shoe having a flat surface portion in contact with an inclined plate integrally rotating with the rotating shaft and a spherical portion fitted in the fitting recess of the piston is interposed between the inclined plate and the piston, and the rotational force of the inclined plate is passed through the shoe. In the inclined plate type compressor provided with a sliding contact membrane in the sliding contact area with respect to the shoe of the inclined plate to transfer the reciprocating motion to the piston, The main chamfering portion is provided on the outer circumferential side of the flat surface portion of the shoe, and the inclination angle of the main chamfering portion with respect to the plane in contact with the center of the flat surface portion is a gentle inclination angle less than a predetermined angle, and the main chamfering portion and the plane An inclined plate compressor, wherein the maximum spacing is less than or equal to the thickness of the sliding contact membrane. The method of claim 1, An inclined plate type compressor comprising: an enclosing portion of the main cutting portion and a parent cutting portion provided to be connected to the main cutting portion, and the inclination angle of the parent cutting portion is larger than the predetermined angle. The method according to claim 1 or 2, And the flat surface portion comprises a convex surface portion and the main chamfer portion having an inclination angle with respect to the plane less than or equal to the inclination angle of the main chamfer portion. The method according to any one of claims 1 to 3, An inclined plate compressor, wherein the predetermined angle is set to 20 °. The method according to any one of claims 1 to 4, And the sliding contact membrane is formed of a metal layer formed on the surface of the sliding contact region of the inclined plate and a resin material containing a solid lubricant formed on the metal layer. The method of claim 5, The inclined plate is made of iron-based material, the metal layer is inclined plate-type compressor, characterized in that the aluminum or copper material.