KR20190061086A - Swash plate compressor - Google Patents

Abstract

In the swash plate type compressor of the present invention, a first sliding layer is formed between the swash plate and each shoe, and a second sliding layer is formed between the cylinder bore and the piston. The first sliding layer and the second sliding layer have a binder resin and a solid lubricant. The contact angle of the lubricant in the first sliding layer is smaller than the contact angle of the lubricant in the second sliding layer.

Description

Swash plate compressor

The present invention relates to a swash plate type compressor.

A general swash plate type compressor includes a housing, a drive shaft, a swash plate, a plurality of shoples, and a plurality of pistons. The housing has a swash plate chamber and a plurality of cylinder bores. The drive shaft is supported by the housing and is rotatable in the swash plate chamber. The swash plate is formed in the swash plate chamber and is rotatable synchronously with the drive shaft. Each pair of shoes slides on the swash plate. Each of the pistons reciprocates in each cylinder bore with a stroke corresponding to the inclination angle of the swash plate through the pair of shoes. A first sliding layer is formed on both sides of the swash plate for sliding each shoe. A second sliding layer is formed on the circumferential surface of the piston sliding on the cylinder bore.

Patent Document 1 discloses a resin material that can be employed in these first and second sliding layers. The resin material is made of a fluorine resin such as polytetrafluoroethylene (PTFE), ultrahigh molecular weight polyethylene, or the like. In this swash plate type compressor, it is conceivable that each of the shoe is appropriately slid with respect to the swash plate by the first sliding layer, and the piston slides appropriately with respect to the cylinder bore by the second sliding layer.

Japanese Laid-Open Patent Publication No. 2010-60262

However, in the case where the swash plate type compressor constitutes a refrigerating circuit for a vehicle together with an evaporator, a condenser and the like, and the lubricating oil is filled in the refrigerating circuit together with the refrigerant, the inventors recognize that the swash plate chamber is provided with a large amount of lubricating oil And a portion where there is not much lubricant oil exists. Particularly, lubricating oil is hardly present between the swash plate and each shoe, and lubricating oil is likely to exist between the cylinder bore and the piston. On the other hand, according to the inventors' perception, a lot of lubricating oil is required between the swash plate and each shoe.

In this respect, if the first sliding layer is formed of the conventional resin material, depending on the selection of the resin material, wear or burning may occur between the swash plate and each shoe, and durability may be impaired have.

SUMMARY OF THE INVENTION The present invention has been made in view of the above conventional problems, and it is an object of the present invention to provide a swash plate type compressor capable of exhibiting excellent durability.

A swash plate compressor according to the present invention comprises: a housing having a swash plate chamber and a plurality of cylinder bores; a drive shaft rotatable in the swash plate chamber supported by the housing; And a piston which reciprocates in each of the cylinder bores with a stroke corresponding to an inclination angle of the swash plate via the shoe and compresses the refrigerant containing lubricating oil,

Wherein a first sliding layer is formed between the swash plate and the shoe and a second sliding layer is formed between the cylinder bore and the piston,

Wherein the first sliding layer and the second sliding layer have a binder resin and a solid lubricant,

And the contact angle of the lubricating oil in the first sliding layer is smaller than the contact angle of the lubricating oil in the second sliding layer.

In the swash plate type compressor of the present invention, the shoe is appropriately slid with respect to the swash plate by the first sliding layer having the binder resin and the solid lubricant, as the experimental results of the inventors show. In addition, the piston is appropriately slid with respect to the cylinder bore by the second sliding layer having the binder resin and the solid lubricant.

Particularly, in this swash plate type compressor, the contact angle of the lubricating oil in the first sliding layer is smaller than the contact angle in the second sliding layer for the lubrication. Therefore, the first sliding layer has higher oil wettability than the second sliding layer. For this reason, it is difficult for the swash plate type compressor to have a lubricating oil. On the other hand, a lot of lubricating oil can be present even between the swash plate and the shoe in which a lot of lubricating oil is required. Therefore, it is difficult to cause abrasion or sintering between the swash plate and the shoe.

Further, in the structure of the swash plate type compressor, lubricating oil is likely to be present, while there is no lubricating oil between the cylinder bore and the piston where a large amount of lubricating oil is not desired. That is, the lubricating oil can be moved between the cylinder bore and the piston to the swash plate chamber, and the lubricating oil can be present between the swash plate and the shoe.

Therefore, in the swash plate compressor of the present invention, excellent durability can be exhibited.

The first and second sliding layers have a binder resin and a solid lubricant. The binder resin exhibits the preservation and maintenance properties of a solid lubricant that makes it difficult to remove the solid lubricant, the durability against the shear force repeatedly acting under the layered coating (base hardness), the abrasion resistance difficult to break, and the heat resistance. As the binder resin, polyamideimide (PAI), polyimide, epoxy resin, phenol resin and the like can be employed. Considering the cost and characteristics, it is optimal to use PAI as a binder resin.

The solid lubricant is retained in the binder resin and exhibits low shear force and low friction coefficient at the outermost surface. As the solid lubricant, fluorine resin, molybdenum dioxide, graphite, ultrahigh molecular weight polyethylene particles and the like can be employed. The fluororesin and ultrahigh molecular weight polyethylene particles improve the slippery property by forming a film on the sliding surfaces of the first and second sliding layers and by transferring them to a counter material. Molybdenum dioxide and graphite improve the slidability by a crystal structure having a low shear force and realize low friction in a high load. According to the results of the inventors' experiments, although the fluororesin has sliding characteristics such as abrasion resistance and abrasion resistance, it has oil repellency, and the contact angle of the lubricant oil is relatively large. On the other hand, the ultrahigh molecular weight polyethylene particles have lipophilicity characteristics, although they are inferior to the fluororesin in the sliding properties, and the contact angle of the lubricant oil is relatively small. As the solid lubricant, soft metal such as melamine cyanurate (MCA), calcium fluoride, copper and tin may be employed.

Further, the first and second sliding layers may have additives besides the binder resin and the solid lubricant. As the additive, hard particles such as titanium dioxide, calcium tertiary phosphate, alumina, silica, silicon carbide, silicon nitride and the like hard particles can be employed which improve the hardness of the first and second sliding layers.

Further, the first and second sliding layers may have a surfactant, a coupling agent, a processing stabilizer, an antioxidant, and the like.

Preferably, the solid lubricant of the first sliding layer comprises ultra-high molecular weight polyethylene and the solid lubricant of the second sliding layer comprises a fluororesin. As described above, since the fluororesin has the oil-releasing property and the ultra-high molecular weight polyethylene has the oil-affinity characteristic, the solid lubricant of the first sliding layer contains the ultra-high molecular weight polyethylene and the solid lubricant of the second sliding layer contains the fluororesin It is possible to surely realize the present invention.

The swash plate type compressor of the present invention exhibits a remarkable action effect when the swash plate chamber is directly connected to the evaporator. That is, in the swash plate type compressor in which the swash plate chamber is directly connected to the evaporator, when the liquid refrigerant in the swash plate chamber is returned from the evaporator, the lubricating oil on the swash plate is liable to flow out by the refrigerant. As a result, the first sliding layer between the swash plate and each shoe tends to be worn, and it is easy to cause the swash plate. On the other hand, in the swash plate type compressor of the present invention, even if the swash plate chamber is directly connected to the evaporator, the lubricating oil on the first sliding layer is difficult to flow by the refrigerant because of the high wettability of the first sliding layer, Since the lubricating oil between the bore and the piston moves to the swash plate chamber and is introduced between the swash plate and the shoe, the lubricating oil is easily supplied between the swash plate and the shoe.

The swash plate type compressor of the present invention has a link mechanism which is formed in the swash plate chamber and allows a change of the inclination angle of the swash plate and a mechanism which is formed in the swash plate chamber and includes an actuator for changing the inclination angle of the swash plate. Effect. Here, the actuator includes: a partition formed to be rotatable integrally with the drive shaft in the swash plate chamber; a movable body which is integrally rotatable with the drive shaft in the swash plate chamber and which moves in the drive shaft direction relative to the partition body to change the inclination angle; A control pressure chamber which is partitioned by the partition body and the moving body and moves the moving body by the pressure inside the partition body and a control mechanism for controlling the pressure in the control pressure chamber.

That is, in the swash plate compressor provided with the link mechanism and the actuator, as compared with the swash plate compressor in which the pressure of the crank chamber is controlled to change the inclination angle of the swash plate, the volume of the swash plate chamber is small, It is difficult to supply lubricating oil to the first sliding layer. As a result, the first sliding layer between the swash plate and each shoe tends to be worn, and it is easy to cause the swash plate. On the other hand, in the swash plate compressor of the present invention, since the first sliding layer has high wettability, the link mechanism and the actuator are provided, and even if the volume of the swash plate chamber is small, the lubricating oil on the first sliding layer is hardly flowed by the refrigerant .

The swash plate type compressor of the present invention can exhibit excellent durability.

1 is a cross-sectional view showing a swash plate type compressor according to a first embodiment.
Fig. 2 is a schematic view showing a swash plate type compressor according to Embodiment 1, showing a control mechanism. Fig.
3 is an enlarged cross-sectional view showing a swash plate compressor, a swash plate, a shoe, and a piston according to the first embodiment.
4 is a schematic sectional view showing a swash plate body and a first sliding layer in the swash plate type compressor of the first embodiment.
5 is an enlarged cross-sectional view of a swash plate type compressor according to Embodiment 1, showing a cylinder bore and a piston.
6 is a schematic sectional view showing a piston body and a second sliding layer with respect to the swash plate type compressor of the first embodiment.

(Mode for carrying out the invention)

Hereinafter, a first embodiment of the present invention will be described with reference to the drawings. In Fig. 1, the left side of the compressor is defined as the front side, the right side is defined as the rear side, the upper side is defined as the upper side, and the lower side is defined as the lower side. Incidentally, all the directions shown in Figs. 3 and 5 are displayed corresponding to the respective directions shown in Fig.

1, a swash plate type compressor (hereinafter referred to as compressor) according to the first embodiment includes a housing 1, a drive shaft 3, a swash plate 5, a plurality of pairs of shoes 7a and 7b, A plurality of pistons 9, a link mechanism 11, an actuator 13, and a control mechanism 15 shown in Fig.

1, the housing 1 has a front housing 17, a rear housing 19, a first cylinder block 21, and a second cylinder block 23. As shown in Fig.

The front housing 17 is located in front of the compressor. The rear housing 19 is located behind the compressor. The first cylinder block 21 and the second cylinder block 23 are located between the front housing 17 and the rear housing 19.

In the front housing 17, a first suction chamber 27a and a first discharge chamber 29a are formed. The first suction chamber (27a) is located on the inner circumferential side of the front housing (17). The first discharge chamber (29a) is located on the outer peripheral side of the front housing (17).

In the rear housing 19, a control mechanism 15 is formed. In the rear housing 19, a second suction chamber 27b, a second discharge chamber 29b, and a pressure adjusting chamber 31 are formed. The second suction chamber (27b) is located on the inner peripheral side of the rear housing (19). The second discharge chamber (29b) is located on the outer peripheral side of the rear housing (19). The pressure adjusting chamber 31 is located at the center portion of the rear housing 19. [ The first discharge chamber 29a and the second discharge chamber 29b are connected by a discharge passage (not shown), and a discharge port (not shown) is formed in the discharge passage.

A swash plate chamber (33) is formed in the first cylinder block (21) and the second cylinder block (23). The swash plate chamber (33) is located approximately at the center of the housing (1). The swash plate chamber 33 is directly connected to an evaporator (not shown) via an intake port 330 formed in the second cylinder block 23. [

In the first cylinder block 21, a plurality of first cylinder bores 21a are formed in a concentric circular shape at regular angular intervals. The first cylinder block 21 is provided with a first shaft hole 21b through which the drive shaft 3 is inserted. The first cylinder block 21 is formed with a first suction passage 37a for communicating the swash plate chamber 33 and the first suction chamber 27a.

A first valve unit 39 is formed between the front housing 17 and the first cylinder block 21. The first valve unit 39 is formed with a suction port 39b and a discharge port 39a in the same number as the first cylinder bore 21a. Each of the first cylinder bores 21a communicates with the first suction chamber 27a through a suction valve (not shown) by the suction ports 39b. Each of the first cylinder bores 21a communicates with the first discharge chamber 29a through a discharge valve (not shown). The first valve unit 39 is formed with a communication hole 39c. The first suction chamber 27a communicates with the swash plate chamber 33 through the first suction passage 37a by the communication hole 39c.

A plurality of second cylinder bores 23a are formed in the second cylinder block 23 in the same manner as the first cylinder block 21. [ The second cylinder block 23 is formed with a second shaft hole 23b through which the drive shaft 3 is inserted. The second shaft hole (23b) communicates with the pressure adjusting chamber (31). The second cylinder block 23 is formed with a second suction passage 37b for communicating the swash plate chamber 33 and the second suction chamber 27b.

A second valve unit (41) is formed between the rear housing (19) and the second cylinder block (23). Like the first valve unit 39, the second valve unit 41 is also formed with a suction port 41b and a discharge port 41a, which are the same number as the second cylinder bore 23a. Each of the second cylinder bores 23a communicates with the second suction chamber 27b via the suction valve 51 (see Fig. 5) by the respective suction ports 41b. Each of the second cylinder bores 23a communicates with the second discharge chamber 29b via the discharge valve 52 (see FIG. 5) by the discharge port 41a. In the second valve unit 41, a communication hole 41c is formed. The second suction chamber 27b communicates with the swash plate chamber 33 through the second suction passage 37b by the communication hole 41c.

The first and second suction chambers 27a and 27b and the swash plate chamber 33 are communicated with each other by the first and second suction passages 37a and 37b. Therefore, the pressures in the first and second suction chambers 27a and 27b and the swash plate chamber 33 are substantially the same (more precisely, due to the influence of blow-by gas, The swash plate chamber 33 is slightly higher in pressure than the first and second suction chambers 27a and 27b. The respective pressures in the swash plate chamber 33 and in the first and second suction chambers 27a and 27b are set such that the refrigerant gas flowing through the suction port 330 flows into the swash plate chamber 33 through the evaporator, 1 and 2 discharge chambers 29a and 29b.

A swash plate 5, an actuator 13, and a flange 3a are attached to the drive shaft 3, respectively. The drive shaft 3 is inserted into the first and second shaft holes 21b and 23b in the first and second cylinder blocks 21 and 23. [ The drive shaft 3 is pivotally supported by the first and second shaft holes 21b and 23b so as to be rotatable about the rotation axis O in the swash plate chamber 33. [

The drive shaft 3 is provided with an axial passage 3b extending forward from the rear end in the direction of the rotational axis O and a path 3c extending in the radial direction from the front end of the axial passage 3b and opened to the outer peripheral surface of the drive shaft 3 Is formed. The rear end of the shaft 3b is open to the pressure adjusting chamber 31. [ On the other hand, the path 3c is open to the control pressure chamber 13c to be described later.

As shown in Figs. 1 and 3, the swash plate 5 has a flat plate shape. The swash plate 5 is composed of a swash plate body 5a and a first sliding layer 5b. On the front and rear surfaces of the swash plate body 5a, a first sliding layer 5b is formed. The swash plate (5) is fixed to the ring plate (45). The ring plate 45 is formed in an annular flat plate shape, and an insertion hole 45a is formed in the center portion. The swash plate 5 is attached to the drive shaft 3 and is disposed in the swash plate chamber 33 by inserting the drive shaft 3 into the insertion hole 45a.

As shown in FIG. 1, the link mechanism 11 has a lug arm 49. The lug arm 49 is disposed in the swash plate chamber 33 and is located further rearward than the swash plate 5. [ The lug arm 49 is formed so as to have a substantially L shape from one end toward the other end.

The one end side of the lug arm 49 is connected to the upper end side of the ring plate 45 by the first pin 47a. The one end side of the lug arm 49 has the first pivot axis M1 as the first pivot axis M1 and the first pivot axis Ml as the first pivot axis Ml, And is pivotably supported around the pivot axis M1.

The other end side of the lug arm 49 is connected to the support member 43 press-fitted to the rear end side of the drive shaft 3 by the second pin 47b. The other end side of the lug arm 49 is connected to the second pivot axis M 2 with respect to the support member 43 or drive shaft 3 with the axis of the second pin 47 b as the second pivot axis M 2 M2. ≪ / RTI >

In this compressor, the swash plate 5 and the drive shaft 3 are connected by the link mechanism 11, so that the swash plate 5 can rotate synchronously with the drive shaft 3. Both ends of the lug arm 49 pivot about the first pivot axis M1 and the second pivot axis M2, respectively, thereby permitting the inclination angle of the swash plate 5 to be changed. That is, the link mechanism 11 is capable of changing the inclination angle of the swash plate 5.

As shown in Figs. 1 and 5, each of the pistons 9 is composed of a piston body 9a and a second sliding layer 9b. On the entire surface of the piston body 9a, a second sliding layer 9b is formed. Each of the pistons 9 has a first piston head 9c on the front end side and a second piston head 9d on the rear end side. The first piston head 9c is reciprocably housed in the first cylinder bore 21a to form a first compression chamber 21d. The second piston head 9d is reciprocably housed in the second cylinder bore 23a to form a second compression chamber 23d. Each of the pistons 9 is formed with a recess 9e.

As shown in Figs. 1 and 3, the shoes 7a and 7b are each formed in a hemispherical shape. Each of the shoes 7a and 7b is formed in each concave portion 9e. The shoes 7a and 7b slide with the swash plate 5. The rotation of the swash plate 5 is converted into the reciprocating motion of the piston 9 by the shoe 7a, 7b. In this way, each piston 9 is moved in the first and second cylinder bores 21a and 23a with a stroke corresponding to the inclination angle of the swash plate 5 through the pair of shoes 7a and 7b It is possible to reciprocate.

1, the actuator 13 is disposed in the swash plate chamber 33 and is located further forward than the swash plate 5. As shown in Fig. The actuator 13 has a partition 13a, a moving body 13b, and a control pressure chamber 13c.

The partition member 13a is formed in a disc shape. The drive shaft 3 is inserted into the partition 13a. The partition member 13a is fixed to the drive shaft 3 and is formed integrally with the drive shaft 3. [

The moving body 13b is located between the flange 3a and the swash plate 5. [ The moving body 13b is formed into a cylindrical shape with a bottom. In addition, the drive shaft 3 is inserted into the moving body 13b. The moving body 13b is rotatable integrally with the drive shaft 3. In addition, a partition 13a is slidably disposed in the moving body 13b. The movable body 13b can move in the direction of the rotation axis O of the drive shaft 3 with respect to the partition body 13a. The moving body 13b faces the link mechanism 11 with the swash plate 5 interposed therebetween. In this way, the actuator 13 can rotate integrally with the drive shaft 3 around the rotation axis O.

At the rear end of the moving body 13b, an attachment portion 13d is formed. The attachment portion 13d is connected to the lower end side of the ring plate 45 by the third pin 47c. The other end side of the ring plate 45 is connected to the lower end side of the ring plate 45, that is, the swash plate 5, with the axial center of the third pin 47c as the third swing axial center M3, And is swingably supported around the swing axis M3. In this way, the moving body 13b is connected to the swash plate 5.

The control pressure chamber 13c is partitioned by the partition body 13a and the moving body 13b. The control pressure chamber 13c communicates with the pressure adjusting chamber 31 through the path 3c and the axial passage 3b. The control pressure chamber 13c moves the moving body 13b by an internal pressure. The moving body 13b moves in the direction of the rotation axis O of the drive shaft 3 with respect to the partition body 13a and the inclination angle of the swash plate 5 can be changed. In other words, the actuator 13 is capable of changing the inclination angle of the swash plate 5.

As shown in Fig. 2, the control mechanism 15 has an extraction passage 15a, an air supply passage 15b, a control valve 15c, and an orifice 15d as control passages. The control mechanism 15 controls the pressure in the control pressure chamber 13c through them.

The second suction chamber 27b communicates with the pressure adjusting chamber 31 through the additional passage 15a. The pressure adjusting chamber 31 communicates with the control pressure chamber 13c via the axial passage 3b and the passage 3c. That is, the second suction chamber 27b and the control pressure chamber 13c are in communication with each other. An orifice 15d is formed in the additional passage 15a, and the flow rate of the refrigerant gas flowing in the additional passage 15a is reduced.

The second discharge chamber 29b communicates with the pressure adjusting chamber 31 through the air supply passage 15b. The pressure adjusting chamber 31 communicates with the control pressure chamber 13c via the axial passage 3b and the passage 3c. That is, the second discharge chamber 29b and the control pressure chamber 13c are in communication with each other. The axial passage 3b and the passage 3c form a part of the additional passage 15a and the air supply passage 15b as control passages.

In the air supply passage 15b, a control valve 15c is formed. The control valve 15c is capable of adjusting the opening degree of the air supply passage 15b based on the pressure in the second suction chamber 27b and adjusts the flow rate of the refrigerant gas flowing through the air supply passage 15b Is possible. The control valve 15c may be a utility product.

As a characteristic construction of the compressor of the first embodiment, a first sliding layer 5b is formed on the front and rear surfaces of the swash plate body 5a as shown in Fig. The swash plate main body 5a excluding the first sliding layer 5b in the swash plate 5 is made of an iron-based metal (iron alloy containing most iron or iron, the same applies hereinafter). The swash plate body 5a may be made of an aluminum-based metal (aluminum or aluminum alloy containing the greatest amount of aluminum, hereinafter the same).

First sliding layer (5b) has, polyamide-imide (PAI) of the binder resin 70 and, ultra high molecular weight polyethylene particles (UHPE), (81), dioxide, molybdenum (MoS ₂₎ (83) As shown in Fig. 4 And graphite (84). These ratios (volume%) are as shown in the sliding layer 1 of Table 1. UHPE has an average particle diameter of 1 to 30 占 퐉 and an average molecular weight of 500,000. When the particle diameter is smaller than 1 占 퐉, handling becomes difficult because of easy condensation, and when it is larger than 30 占 퐉, the surface roughness of the layer becomes large and the sliding performance deteriorates. When the molecular weight is less than 500,000, the abrasion resistance is deteriorated.

The shoe 7a, 7b sliding on the sliding surface of the first sliding layer 5b is also made of an iron-based metal. The shoes 7a and 7b may be aluminum-based metals. The shoes 7a and 7b may be formed of the shoe main body and the first sliding layer 5b.

On the entire surface of each piston 9, as shown in Fig. 5, a second sliding layer 9b is formed. The piston body 9a excluding the second sliding layer 9b in the piston 9 is made of an aluminum-based metal. The piston body 9a may be an iron-based metal.

As shown in Fig. 6, the second sliding layer 9b has a binder resin 70 that is a PAI and a PTFE 82 that is a solid lubricant. The ratios (volume%) thereof are as shown in the sliding layer 4 in Table 1. That is, the solid lubricant is composed only of the PTFE 82.

The first and second cylinder blocks 21 and 23 that slide with the sliding surface of the second sliding layer 9b are made of an aluminum-based metal. The first and second cylinder blocks 21 and 23 may be iron-based metals. It is also possible that the first and second cylinder blocks 21 and 23 are composed of the first and second cylinder block bodies and the second sliding layer 9b.

The first and second sliding layers 5b and 9b are formed as follows. First, each solid lubricant is blended into the PAI varnish and disturbed. Then, the mixture is passed between three roll mills to obtain a paint. The coating material may optionally be selected from the group consisting of n-methyl-2-pyrrolidone, 1,3-dimethyl-2-imidazolidinone (for example, , Or diluted with a solvent such as xylene. Then, the swash plate body 5a and the piston body 9a are coated with a paint, followed by drying and firing (230 deg. C for 1 hour). The film thus obtained is adjusted to a thickness of 20 mu m to form the first and second sliding layers 5b and 9b.

In the thus-obtained compressor of the first embodiment, a pipe connected to the evaporator is connected to the suction port 330 shown in Fig. 1, and a pipe connected to a condenser (not shown) is connected to the discharge port. A refrigerating circuit of a car air conditioner is constituted by a compressor, an evaporator, an expansion valve, a condenser and the like.

In this compressor, as the drive shaft 3 rotates, the swash plate 5 rotates, and the pistons 9 reciprocate within the first and second cylinder bores 21a and 23a. For this reason, the first and second compression chambers 21d and 23d cause a volume change in accordance with the piston stroke. The refrigerant gas sucked into the light shaft 33 by the suction port 330 from the evaporator flows through the first and second suction chambers 27a and 27b into the first and second compression chambers 21d and 23d And is discharged to the first and second discharge chambers 29a and 29b. The refrigerant gas in the first and second discharge chambers (29a, 29b) is discharged from the discharge port to the condenser.

Meanwhile, in this compressor, each of the shoes 7a and 7b slides with respect to the swash plate 5 appropriately by the first sliding layer 5b. Further, the pistons 9 slide appropriately with respect to the first and second cylinder bores 21a and 23a by the second sliding layer 9b.

Particularly, in this compressor, since the first sliding layer 5b has a higher wettability than the second sliding layer 9b, lubricating oil is supplied from the cylinder bores 21a, 23a and the piston 9 to the swash plate chamber 33, So that the amount of lubricating oil can be increased between the swash plate 5 and the shoes 7a and 7b. Therefore, even between the swash plate 5 and the shoes 7a and 7b, a large amount of lubricating oil can be present. Therefore, it is difficult to cause abrasion or sintering between the swash plate 5 and the shoes 7a and 7b.

Further, between the first and second cylinder bores 21a and 23a and the respective pistons 9, it is possible to prevent the lubricating oil from being present. Therefore, it is possible to move the lubricating oil between the first and second cylinder bores 21a and 23a and the pistons 9 to the swash plate chamber 33.

Therefore, the compressor of the first embodiment can exhibit excellent durability.

(exam)

In order to confirm the effect of the first embodiment, each test piece having the sliding layers 1 to 5 was prepared. The substrate corresponding to the swash plate body or the piston body in each test piece is cast iron. The ratios (volume%) of the binder resin and the solid lubricant in the sliding layers 1 to 5 in the respective test pieces are as shown in Table 1. Each specimen has the same mass.

Table 2 shows the basic properties of the fluororesin (PTFE) and the ultra high molecular weight polyethylene particles (UHPE) constituting the composition of the sliding layers 1, 2, 4 and 5.

The contact angles of the lubricating oil in the sliding layers (1 to 5) of the respective test pieces are as shown in Table 1. Here, as the lubricating oil, polyalkylene glycol (PAG) was used. As the lubricating oil, polyol ester (POE) or the like may be used. From Table 1, it can be seen that the sliding layers 1 and 2 have a lipophilic property in that the contact angle is small. On the other hand, the sliding layers 4 and 5 have a fluidity characteristic in that the contact angle is larger than that of the sliding layers 1 and 2.

Further, the sliding layers 1 to 3 of the respective test pieces were subjected to the following Tests 1 and 2.

Test 1: Ring-on-Disc Evaluation

The coefficient of friction and the ratio of abrasion wear were determined under the conditions of no lubricating (no lubricating oil), slip speed of 9 m / sec, and load of 220 N, using S45C for the relative ring material.

Test 2: Swash plate / shoe, step load baking evaluation

Under the conditions of oil lubrication (with lubricating oil: refrigerator oil was attached to the surface of the swash plate at 25 g / min), load 400 N was applied every 5 minutes and the number of revolutions was 1500 rpm. The load caused by the burning was obtained. The results are shown in Table 3.

The sliding layers 1 and 2 have a lower coefficient of friction, less friction, and improved sealing performance as compared with the sliding layer 3. This is because the sliding layers 1 and 2 contain UHPE as a solid lubricant.

In addition, the solid lubricant of the sliding layers 1 and 2 contains UHPE, whereas the solid lubricant of the sliding layers 4 and 5 does not contain UHPE, and instead contains PTFE. Therefore, the sliding layers 1 and 2 including UHPE have less abrasion and improved wear resistance as compared with the sliding layers 4 and 5 including PTFE. Thus, it can be seen that the sliding layers 1 and 2 have a high lipophilic property and an improved oil-wettability to form an oil film and have excellent abrasion resistance.

Although the present invention has been described based on the first embodiment and the first and second tests, the present invention is not limited to the first embodiment, and it is possible to appropriately change and apply the present invention without departing from the spirit of the present invention Not to mention.

(Industrial availability)

The present invention can be used in an air conditioner or the like.

1: Housing
3:
5: Swash plate
5b: a first sliding layer
7a, 7b: Shoe
9: Piston
9b: second sliding layer
11: Link mechanism
13: Actuator
13a:
13b:
13c:
15:
33: swash plate
21a: first cylinder bore (cylinder bore)
23a: second cylinder bore (cylinder bore)
70: binder resin
81: UHPE (Ultra High Molecular Weight Polyethylene)
82: PTFE (fluororesin)

Claims (3)

A swash plate supported in the housing and rotatable in the swash plate chamber; a swash plate formed in the swash plate chamber and capable of being rotated synchronously with the drive shaft; and a swash plate And a piston reciprocating in each of the cylinder bores with a stroke corresponding to an inclination angle of the swash plate through the shoe to compress a refrigerant containing lubricating oil,
Wherein a first sliding layer is formed between the swash plate and the shoe and a second sliding layer is formed between the cylinder bore and the piston,
Wherein the first sliding layer and the second sliding layer have a binder resin and a solid lubricant,
Wherein the solid lubricant of the first sliding layer comprises ultra-high molecular weight polyethylene, the solid lubricant of the second sliding layer comprises a fluororesin,
Wherein the contact angle of the lubricant in the first sliding layer is smaller than the contact angle of the lubricant in the second sliding layer. The method according to claim 1,
Wherein the swash plate chamber is directly connected to the evaporator. 3. The method of claim 2,
A link mechanism which is formed in the swash plate chamber and permits the inclination angle of the swash plate to be changed; and an actuator which is formed in the swash plate chamber and changes the inclination angle of the swash plate,
Wherein the actuator comprises: a partition formed integrally with the drive shaft in the swash plate chamber; and a swash plate rotatable integrally with the drive shaft in the swash plate chamber. The actuator moves in the direction of the drive shaft with respect to the partition, A control pressure chamber which is partitioned by the partition and the moving body to move the moving body by an internal pressure and a control mechanism that controls a pressure in the control pressure chamber.

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