Compressor

Mode of execution

The following, based on Figure 1-Figure 3 shows that section 1 embodiment of a variable-capacity inclined-plate compressor (the following, single-referred to as the compressor).

As shown in Figure 1, with a shell of the compressor in a joint in the cylinder block 11 on the front end of the front housing part 12, and by means of a valve-to-end lip-adult 13 engaged in the cylinder block 11 on the rear end of the rear housing part 14. In the cylinder block 11 and the front housing member 12 in an area surrounded by a divided into crank chamber 15. In the crank chamber 15 the inner, rotatably provided with the drive shaft 16. The drive shaft 16 and the mounting of the engine on a vehicle 17 connecting action, from the engine 17 rotates under the supply of power.

In the crank chamber 15 in, when the drive shaft 16 with the drive shaft 16 is rotating integrally with a connecting plate 18. Furthermore, in the crank chamber 15 is accommodated in the swash plate 19. The swash plate 19 by the drive shaft 16 the support, can be along the drive shaft 16 in the axis of the drive shaft 16 to slide on, and can be with respect to the drive shaft 16 the tilting. The patch board 18 and the swash plate 19 is sandwiched between the hinge mechanism 20. The swash plate 19 through the hinge mechanism 20 and the wiring board 18 and a drive shaft 16 to rotate in synchronism, and it can be on one side with the drive shaft 16 while moving to the axial direction of the tilting. Furthermore, the swash plate 19 by the latter of the angle of incidence of the capacity control valve 21 control.

The cylinder block 11 are formed in a plurality of (in fig. 1 only in that 1 a) cylinder bores 11a, in the cylinder bore 11a in a reciprocating movement to the piston single end 22. Each of the piston 22 via the washer 23 seizing in the swash plate 19 on the peripheral part. Therefore, with the drive shaft 16 the rotation of the swash plate 19 by the rotary motion of the back strap 23 is converted to a piston 22 reciprocating straight-line motion.

In the cylinder bore 11a the back side (in Figure 1 is in the right), is divided by the piston 22 and the valve-to-end lip-adult 13 surrounds the discharge chamber 24.

In the rear housing part 14 with the suction chamber 25, and in the suction chamber 25 with the periphery of the discharge chamber 26.

The suction chamber 25 through the refrigerant gas in piston 22 downward from the top dead center position a dead center position by the movement of the valve-to-end lip-adult 13 on the suction port 27 and the suction valve 28 is sucked into the compression chamber 24 in. Is sucked into the compression chamber 24 through the gas coolant in the piston 22 from bottom dead center position to the top dead center position and is compressed to the established pressure, and by forming in the valve-to-end lip-adult 13 of the discharge port 29 and the discharge valve 30 is discharged to discharge chamber 26 in.

In the shell is provided with a pumping passage 31 and air supply passage 32. Air suction path 31 is used to from the crank chamber 15 to the suction chamber 25 is derived passage of refrigerant gas. Air supply passage 32 is used for the discharge chamber 26 discharges the coolant in the gas introduced into the crank room 15 path. In the air supply passage 32 is arranged midway of the capacity control valve 21.

By the adjustment of the capacity control valve 21 opening, control via the air supply passage 32 into the crank chamber 15 in the introduction amount of the high-pressure coolant gas, and via the air suction path 31 from the crank chamber 15 of the coolant gas is derived the balance derived euqntity , decides a crank chamber 15 of the pressure.

Therefore, the alteration by the piston 22 of the crank chamber 15 and the pressure of the liquid in the compression chamber 24 is the pressure in the, change of swash plate 19 with respect to the drive shaft 16 the angle of inclination of. As a result, changing the piston 22 stroke, the discharge capacity of the compressor.

For example, if the crank chamber 15 to reduce the internal pressure of the swash plate 19 to increase the angle of inclination of, increasing the discharge capacity of the compressor. Figure 1 is shown in two-dot chain line of the swash plate 19 said inclined angle is maximum. On the contrary, if the crank chamber 15 of the internal pressure of the swash plate 19 to reduce the angle of inclination of the, reducing discharge capacity of the compressor. Figure 1 shown in the solid line of the swash plate 19 that the state of the minimum inclination angle.

As shown in Figure 1 and Figure 2 as shown, in the rear housing member 14 is connected to the upper portion of the discharge chamber 26 is cylinder hole 33. cylinder hole 33 is formed in the discharge chamber 26 of the discharge passage. cylinder hole 33 and the drive shaft 16 extending parallel to the axis of. The cylinder hole 33 of the axial central portion provided with a cylindrical oil separator 35. Oil separator 35 by making the cylindrical portion 35a towards the front, to make than the cylindrical portion 35a large diameter of the pedestal part 35b is embedded in the cylinder hole 33 is fixed to the cylinder hole in the 33 upper. Furthermore, the cylinder hole 33 on the central inset clearance ratio of the deep side (in Figure 2 is in the right side), adjacent to the oil separator 35 and containing a check valve 36. Check valve 36 is used to prevent the refrigerant from the external coolant loop 48 to the discharge chamber 26 of the body of the valve.

The cylinder hole 33 of the film (in Figure 2 is in the left side), than with cylinder hole 33 the diameter of the large diameter of the ring 33a. Therefore, the cylinder hole 33 of the inner wall 33b difference department is formed. The cylinder hole 33 is provided with entrance part of the discharge chamber 26 and cylinder hole 33 spaced apart cover 34. Cover 34 is provided with a flange part 34a and win 34b, the cover 34 on the outer peripheral surface of the, through the flange portion 34a and win 34b difference department are formed. Cover 34 through the ring 34b embedded in the cylinder hole 33 of the inner wall 33b is, the flange part 34a is embedded in the ring 33a is fixed to the cylinder in the hole 33 in. Furthermore, the flange part 34a of the axial direction of the size of the set to be less than the thickness of ring e 33a the direction of the axis of the depth dimensions of the small f (e<f).

By the cover 34, oil separator 35, cylinder hole 33 of the inner wall 33b is formed in a space surrounded by a separation chamber 42. Discharge chamber 26 and the separation chamber 42 via the lead-in passage 40 is connected with, is discharged through the refrigerant gas lead-in passage 40 from the discharge chamber 26 to the separation chamber 42 into the.

As shown in Figure 3, lead-in passage 40 is, the is introduced into the separation chamber 42 in the streamline of the discharge refrigerant gas into separation chamber 42 of the inner wall 33b of the cross section of roughly tangent of the circle. Therefore, through the lead-in passage 40 is to the separation chamber 42 discharges the coolant gas along the inner wall 33b clockwise wound.

In the separation chamber 42 in, through the discharges the coolant gas along the inner wall surface 33b of the inner wall surface 33b and the oil separator 35 the cylinder part 35a wound in the space between, the oil discharges the coolant gas from the discharge of the centrifugal separation of the refrigerant gas. The oil separated from the refrigerant gas is discharged from the separation chamber 42 through the oil separator 35 of the internal line 35c introduced into the check valve 36 in, through the discharge passage 41 is to discharge flange 43 in the direction of discharge. Furthermore, line 35c the oil separator 35 through along its length direction, with the cover 34 opposite the position of the front end portion of the upper in the separation chamber 42 in an opening. The presence of the separation blade 42 of the bottom portion 34 near the lower part of the.

The cover 34 are fitted in the cylinder hole 33 in a state, the cover 34 of the outer circumferential surface of the separating chamber difference department 42 of the inner wall 33b of the form the annular space between difference department 37. Annular space 37 is formed on the lid 34 around the four sides of the cross section of the annular grooves. Annular space 37 as communicated with the separation chamber 42 of function fuel in hand department.

Furthermore, the cover 34 and at the lower part of the cover 34 outputs of 34b chimeric separation chamber 42 of the inner wall 33b is formed on the step of a certain width 33c, through the step 33c form, make separation chamber 42 and the ring-shaped space 37 is connected with the throttle passage 38. Therefore, the separate and discharges the coolant gas accumulated in the separation chamber 42 the oil on the bottom portion through the throttling path G 38 to the annular space 37 flows in the direction.

In Figure 1 in, the cylinder block 11 on the upper surface of projecting to the outside is provided with a discharge flange 43. The discharge flange 43 in the interior of, formed with a high pressure fluid chamber 44 and the low pressure fluid chamber 45, in these fluid chamber 44, 45 is arranged between the throttle portion 46. In the low-pressure fluid chamber 45 is arranged at the lower part of oil used for etc 47.

High-pressure fluid chamber 44 through the discharge passage 41 is communicated with the separation chamber 42, the low-pressure fluid chamber 45 via the not shown is connected with the port to the external coolant loop 48. Therefore, from the separation chamber 42 through the discharges the coolant gas discharged from the discharge passage 41 is introduced into the high-pressure fluid chamber 44 in, via the throttle 46 flows into the low-pressure fluid chamber 45 in.

The oil reservoir chamber 47 and the ring-shaped space 37 via fairway 39 is connected. Therefore, separation chamber 42 and the oil reservoir chamber 47 via the throttle passage 38, annular space 37 and the oil path 39 is connected. The oil reservoir chamber 47 via the not shown oil return path is communicated with the crank chamber as a low pressure region 15, and the like.

Furthermore, if the above-mentioned as to the role of a note by the compressor.

First of all, if the compression of the refrigerant gas from the discharge chamber 26 is discharged, then the discharged through the refrigerant gas lead-in passage 40 is to the separation chamber 42 into the. Is to the separation chamber 42 into the side of the discharge coolant gas along the inner wall surface 33b of the inner wall surface 33b and the oil separator 35 the cylinder part 35a wound in the space between, on one side toward the cylindrical portion 35a at the front end of the flow. At this moment, the refrigerant gas contained in the discharge of the oil in the mist under the action of centrifugal force to separate from the coolant gas. After separation of the refrigerant into the oil by the influence of the gas and in the separation chamber 42 wound in, but a part of the gravity along the separating chamber 42 the inner wall 33b Cascaded, storage in the separation chamber 42 of the bottom portion 34 near the lower part of the.

The oil separated from the oil separator discharges the coolant gas 35 cylindrical part 35a through the front end part of the line 35c is introduced into the check valve 36 in. The oil separated in the discharges the coolant gas is introduced into the check valve 36 of the rear, through the discharge passage 41 is to discharge flange 43 in the direction of discharge. And, is introduced into the discharge flange 43 of the high pressure fluid chamber 44 flows into the discharges the coolant gas in the low-pressure fluid chamber 45 in, then through the discharge port is supplied to the external coolant loop 48 in.

Accumulated in the separation chamber 42 G the bottom part of the oil through the throttling passage 38 to the annular space 37 flows in the direction. The annular space 37 and the oil reservoir chamber 47 is connected with, the oil reservoir chamber 47 and the discharge chamber 26 the pressure of the low pressure of the low-pressure region of the crank chamber 15 is communicated with and the like. Therefore, in the separation chamber 42 and the oil reservoir chamber 47 to generate a pressure difference between the between ΔP. In other words, in the discharge chamber 26 is communicated with the separation chamber 42 than the pressure within the oil reservoir chamber 47 is higher than the pressure within. Through this pressure difference the role of Δ P, from the separation chamber 42 flows into the annular space 37 of the oil in the annular space 37 rise in, through fairway 39 to the oil reservoir chamber 47 flows into the direction.

Stored in the oil reservoir chamber 47 through the not illustrated the oil in the oil return path to return to the crank chamber 15 and the like, used for the lubrication of the sliding part of the compressor.

As described in detail above, according to the present embodiment, the following advantages can be obtained.

(1) the oil separator 35 is disposed in the discharge chamber 26 of the cylinder hole (discharge passage) 33 in, through the cylinder hole 33 for the inlet part of the cover 34 to form a separating chamber in the block 42. And, the cover 34 are formed on the periphery of the annular space 37, and set up the annular space 37 and the separation chamber 42 is connected with the throttle passage 38. Therefore, can utilize the separation chamber 42 and the oil reservoir chamber 47 of the pressure difference ΔP between, the storage in the separation chamber 42 G the oil in through the annular space 37 to the separation chamber at 42 on the top of the oil reservoir chamber 47 flows out in the direction of. Therefore, annular space can be freely set, 37, and the annular space 37 and the oil reservoir chamber 47 connected fairway 39 of the path diameter. As a result, can improve the oil reservoir chamber 47 degree of freedom of the disposition of, can realize the miniaturization of the compressor.

(2) through the annular space 37 and the separation chamber 42 is connected with the throttle passage 38, can be prevented from separation chamber 42 to the oil reservoir chamber 47 of the high-pressure of the inflow of the coolant gas is discharged, the oil can only through G.

(3) the discharge chamber 26 with the separation chamber 42 is provided with a cover between 34, can make the separation of oil is not G to the discharge chamber 26 flows in the direction while the memory in the separation chamber 42 of the bottom portion 34 near the lower part of the. As a result, the stored oil can be efficiently G to the oil reservoir chamber 47 is discharged in the direction of.

(4) through the cover 34 and the outer peripheral surface of the separation chamber 42 formed difference department the inner wall surface of the annular space 37, therefore, does not need to be in order to form the annular space 37 and carry out special processing, the processing is relatively simple, it is possible to reduce the processing time.

(5) because only through in the separation chamber 42 of the inner wall 33b is provided difference department 33c and form, make separation chamber 42 and the ring-shaped space 37 is connected with the throttle passage 38, so the processing is relatively simple, it is possible to reduce the processing time.

Furthermore, based on Figure 4 the section 2 of the compressor of the embodiment.

This embodiment mode change section 1 of the embodiment of the separation chamber 42 and the ring-shaped space 37 is communicated with the shape of the throttle passage, other structure is common. Therefore, here, in order to facilitate description, the earthing of parts used in the note in front of the label, the structure of the common description thereof is omitted, only a description of the part of the change.

As shown in Figure 4, the embodiment of the throttling path 51 along the perpendicular to the cover 34 in the direction of the axial line of the (in fig. 4 is in the direction of up and down) provided in the cover extending 34 outputs of 34b of the most of the lower part of the through hole 52 is formed. Through the throttling passage 51 the separation chamber 42 and the ring-shaped space 37 is connected. Therefore, from the discharges the coolant gas separation and storage in the separation chamber 42 G the bottom part of the oil through the throttling passage 51 to the annular space 37 flows in the direction.

According to the embodiment, in addition to the section 1 of the embodiment (1)-(4) other than the advantages of, but also can obtain the following advantages.

(1) through the cover 34 outputs of 34b is provided with a through-hole 52, forming the separation chamber 42 and the ring-shaped space 37 is connected with the throttle passage 51. Does not need to be in order to form a throttle passage 51 and the shell of the compressor, as long as processing cover 34 can be, so the processing is relatively simple.

Furthermore, based on Figure 5 the section 3 of the compressor of the embodiment.

The embodiment of the change of the compressor section 1 embodiment of a cover 34 and the oil separator 35 shape, other structure is common. Therefore, here, in order to facilitate description, the earthing of parts used in the note in front of the label, the structure of the common description thereof is omitted, only a description of the part of the change.

As shown in Figure 5, in the embodiment of a compressor, the separation chamber 42 and the discharge chamber 26 of the cover 62 and the oil separator 35 is integrally formed. Speaking in detail, the part 61 from separating the separation chamber 42 and discharge chamber 26 of the cover 62, with oil separator 35 of the cylindrical part of the function of the 63, and keep the cylindrical part 63 the pedestal part 64 form. In the part 61 is arranged in the inside of the pipeline 65, line 65 to the rear (in Figure 5 in the direction to the right) the opening.

The components 61 the pedestal part 64 in the check valve 36 is installed in the pipeline 65 under the state of the opening side of the as shown in Figure 5, is inserted into the cylinder hole 33 in. The pedestal part 64 is embedded in the inner wall 33b is, through the cover 62 of the ring 62b is embedded in the inner wall 33b is, the flange part 62a is embedded in the ring 33a in, the component 61 is fixed to the cylinder hole 33 in. Furthermore, flange portion 62a of the axial direction of the size of the set to be less than the thickness of ring e 33a the direction of the axis of the depth dimensions of the small f (e<f).

In the cover 62, cylindrical part 63, pedestal part 64 and inner wall 33b in the annular space surrounded by the formed with a separation chamber 42. Discharge chamber 26 and the separation chamber 42 via the lead-in passage 40 is connected. In the part 61 of the cylindrical part 63 is, to the line 65 in a direction crossing the central axis of the separation chamber forming extension 42 and line 65 is communicated with the gas passage hole 63a, and in the separation chamber 42 of the upper opening. In this embodiment, gas passage hole 63a to the pipeline 65 orthogonal to the axis line of the center of the extending direction.

The cover 62 on the outer peripheral surface of, the flange part 62a and win 62b difference department are formed. In the part 61 is fixed to the cylinder hole 33 in a state, the cover 62 of the outer peripheral surface of and difference departmentcylinder hole 33 of the inner wall 33b difference department of piling up as oil is formed between the annular space 37. Annular space 37 is formed in the cover 62 around the four sides of the cross section of the annular grooves. Annular space 37 as the separating chamber 42 the oil storage unit is connected with play to function.

In the above-mentioned, in a compressor, from the discharge chamber 26 from the coolant gas is discharged through the lead-in passage 40 is to the separation chamber 42 into the. Is to the separation chamber 42 into the side of the discharge coolant gas along the inner wall surface 33b of the inner wall 33b of the cylindrical part 63 wound in the space between, while towards the cylindrical part 63 at the front of the flow. At this moment, the refrigerant gas contained in the discharge of the oil in the mist under the action of centrifugal force to separate from the coolant gas. Each of the separated oil by the impact of the coolant gas in the separation chamber 42 wound in, under the action of a part of the weight along the separating chamber 42 the inner wall 33b drop, storage in the separation chamber 42 of the bottom portion 62 near the lower part of the.

The oil is separated through the discharges the coolant gas is formed on the cylindrical part 63 the gas passage in front of the hole 63a flows into the internal of the pipeline 65 of the rear, is introduced into the check valve 36 in. Is introduced into the check valve 36 through the discharges the coolant gas in the discharge passage 41 is to discharge flange 43 in the direction of discharge.

Accumulated in the separation chamber 42 G the bottom part of the oil through the throttling passage 38 to the annular space 37 flows in the direction of, in the separation chamber 42 and the storage chamber 47 between the under the action of pressure difference Δ P, in the annular space 37 to rapidly rise in the oil reservoir chamber 47 flows into the direction.

According to the embodiment, in addition to the section 1 in the embodiment of (1)-(5) other than the advantages of, but also can obtain the following advantages.

(1) because the separation chamber 42 and the discharge chamber 26 of the cover 62 and with oil separator 35 of the functions of the cylindrical part 63 and base 64 are integrally formed in order to make it form a single unit 61, so that the number of parts can be reduced, and that can make the assembling is simplified.

Figure 6 of the section 4 of the compressor to change the mode of execution of the relevant section 1 of the compressor of the embodiment method of forming the annular space, to the section 1 of the embodiment is the same as the structure of the compressor to the same as the label, detailed description is omitted.

In Figure 6 in, formed on the rear housing part 14 cylinder hole on 33 of the inlet part of the inner wall 33b is, four sides are formed the shape of the cross section of the annular groove 71. Annular groove 71 with the fairway 39 is communicated with the position of the. Cover 72 has a certain with in the axial direction of the outer diameter of the ring of 72a, does not have the flange part.

Therefore, through the cover 72 of the ring 72a is fitted to the inner wall 33b is, in the annular groove 71 and the outer ring part 72a is formed between the outer peripheral surface of the annular space as oil storage unit 37. The annular space 37 as communicated with the separation chamber 42, the oil piling up play to function.

Furthermore, annular groove 71 also can replace the rear housing member 14 and formed in the ring 72a on the outer peripheral surface.

Section 4 as long as the compressor of the embodiment of the annular space 37 only the time of forming the rear housing part 14 or cover 72 processing on any one of a ring-shaped groove 71 can be, therefore, can look forward to processing time reduction.

Figure 7 as shown in section 5 of the compressor to change the mode of execution of the section 3 as in the embodiment of the oil storage part of the structure of the annular space, to the relevant section 3 of the compressor in the embodiment of the structure of the compressor is the same as the same label to omit detailed description.

In Figure 7 the, cover 74 and by the cylindrical part 75 and base 76 of the oil separator 35 as a whole to form part of a 73. Part 73 formed on the oil separator 35 in the interior of the pipe line 77 the opening side (the right side of the Figure) is provided with a check valve 36 disposed in the cylindrical part of the 33 in. Cover 74 to flange-shaped form, cylindrical part 75 has a large diameter section 75a and the small diameter section 75b, the small diameter section 75b disposed in the cover 74 and the large diameter section 75a between.

Cylindrical portion 33 in the discharge chamber 26 on one side of the opening of the ring has a large diameter of the 33a. The ring 33a extend in the axial direction to the cylindrical portion 75 of the large diameter section 75a in the vicinity. Therefore, by the part 73, cylinder hole 33 of the ring 33a and inner wall 33b of divided separation chamber 78 of the cover 74 side is formed in a region other than the expanded annular space 79. Annular space 79 is communicated with the separation chamber as 78 play a function of the oil storage unit.

Part 73 through the base 76 pressed into the inner wall 33b in, the cover 74 into the ring 33a is fixed to the cylinder in the hole 33 in. Along with line 77 at right angles to the central axis extending in the direction of the gas passage hole 75c the small diameter section 75b is arranged 4 is, in the separation chamber 78 in an opening. Gas passage hole 75c arrangement position is preferably as far as possible close to the large diameter section 75a. Furthermore, oil passage 39, as oil storage portion of the annular passage 79 direct the upper most part of the opening, for applying the established setting of the throttle in order to make the separation chamber 78 of the high-pressure refrigerant gas will not be to the oil reservoir chamber 47 the size of the side. The discharge chamber 26 and the separation chamber 78 is communicated with the introduction passage, and the coolant gas 49 relative to the line 77 is inclined to the central axis of the cylinder hole 33 of the rear housing part 14 is, points to the cylindrical portion 75 of the large diameter section 75a and the opening.

Formed in the section 5 in a compressor of the embodiment, from the discharge chamber 26 via the lead-in passage 40 into the separation chamber 78 the high-pressure coolant gas in the section 1 embodiment similarly of the large diameter section 75a wound around, will be contained in the coolant gas of the centrifugal separation of the oil in. After the separation of the oil side of the annular space 79 wound one side of the pool to the cover 74 and ring 33a in the vicinity of the wall. A portion of oil that falls in weight, also accumulating in the annular space 79 at the lower part of (Figure 7 below).

Connected to one side of one side of the annular space 79 the upper part of the (Figure 7 above of) G in the vicinity of the wall surface of the oil under the action of the pressure difference by fairway 39 to the oil reservoir chamber 47 in. Furthermore, stacking the annular space 79 of the oil on the wall surface at the lower part of the annular space is G 79 gradually rolled up the twisted stream, from the oil passage 39 discharges sequentially to the oil reservoir chamber 47 in.

In the separation chamber 78 the oil in the coolant gas is separated from the gas passage hole 75c flows into the line 77 in, according to the pressure of the refrigerant gas, the check valve 36 to the Figure 7 to push the right, from the discharge passage 41 to the external coolant loop 48 (with reference to Figure 1) flow.

Subsection 5 embodiment of a compressor in addition to the section 3 the advantages of the other embodiments, also has the following advantages.

(1) through the annular space 79 towards cylinder hole 33 expand the direction of radius of the, oil which has accumulated G the cover 74 and ring 33a from the position of the wall surface of the gas passage hole 75c to leave. Therefore, the oil can be suppressed by G after separation of the refrigerant gas to the line 77 into the phenomenon, can be reduced to an external coolant circuit flows into 48 the coolant gas in the oil concentration.

(2) because the gas passage hole 75c which forms the oil separator is formed 35 of the cylindrical part of the 75 of the small diameter section 75b is, it is possible to shorten the gas path hole 75c length, can be reduced to the line 77 the inflow of pressure loss of the cooling medium gas.

(3) because the member 73 through the press-fit fixing the cylinder hole 33 is, therefore, even if the thin cover 74 and pedestal part of the thickness of the 76 also the thickness of the stable fixing state can be ensured. Therefore, the separation chamber 78 formed so as to be long, the separating capacity of the oil. Furthermore, the sealing member is not required, the number of parts can be reduced.

Figure 8 shown in section 6 of the compressor to change the mode of execution of the section 1 embodiment of a cover 34 of the structure, to the relevant section 1 of the embodiment is the same as the structure of the compressor to the same as the label, detailed description is omitted.

In Figure 8 in, cylinder hole 33 of the inner wall 33b in the axial direction has a certain diameter, the discharge chamber 26 of the upper opening. Cover 80 by the thin-walled iron plate by punching the formed sheet form, has a cylindrical ring 81. Furthermore, cover 80 is not limited to the material of the iron plate, can be replaced as the other a rigid material, can also be formed by molding. Outputs 81 in the part disposed in the rear housing 14 on the upper part of the (Figure 8 above of) fairway of 39 with on the position corresponding to the throttling passage 82, as the cover 80 is fixed to the inner wall by press 33b is on, oil passage 39 with the throttling passage 82 consistent.

Furthermore, in Figure 8 in, the throttling passage 82 and the oil passage 39 is formed to the same diameter, but as long as the throttling passage 82 is able to give full play to the size of the throttling effect, oil passage 39 may be formed than the throttling passage 82 in order to easy processing and of large diameter oil is easy to flow. Cover 80 from the discharge chamber 26 to the throttle path side end surface 82 need is to have the length of the discharge chamber 26 with the following separation chamber 83 between the length of the sealing function of the, but preferably the length of the short as far as possible, corps passage 82 of the inlet as far away as possible from the line 35c inlet 35d.

Through the mounting of the check valve 36 of the oil separator 35 the pedestal part 35b into the cylinder hole 33 in, the lid 80 outputs of 81 pressed into the cylinder hole 33 in, the oil separator 35 and the cover 80 is formed between the separation chamber 83, and along the cover 80 outputs of 81 is formed with the inner peripheral surface of the oil storage part 84. The oil storage part 84 is communicated with the separation chamber as 83 play a function of the oil storage unit.

In section 6 in the compressor of the embodiment, a discharge chamber 26 of the high-pressure refrigerant gas through the lead-in passage 40 is supplied to the oil separator 35 the cylinder part 35a in, around the wound around one side of the to the cover 80 side of the centrifugal separation of the oil. The oil separated from the coolant gas inlet 35d to the line 35c flows, through its pressure the check valve 36 open, to the discharge passage 41 flow. The oil separated from the coolant gas by turns on lathe the circumferential flow G the impact of the refrigerant gas, the oil storage part 84 wound around, and under the action of a part of the weight of accumulated in the oil storage part 84 at the lower part of the (Figure 8 below). Therefore, in the oil of the encircled in Figure 8 the G the upper part of the oil under the action of the pressure difference through the throttle passage 82 to the oil passage 39 in, to the oil reservoir chamber 47 (with reference to Figure 1) is discharged.

Section 6 embodiment of a compressor has the following advantages.

(1) because the oil storage part 84 G wound in the oil under the action of the pressure difference is to the oil passage 39 discharge, therefore, the oil reservoir chamber 47 relatively high degree of freedom of the disposition of, can realize the miniaturization of the compressor.

(2) because the cover 80 is formed is made thin, so can make the separation chamber 83 is relatively long, can inhibit the separation of the oil and coolant gas to the line 35c into the phenomenon.

Figure 9 shown in the section 7 of the embodiment of the change of the compressor section 1 embodiment and 6 embodiment of the structure of the cover of the compressor, to the section 1 embodiment and 6 of the embodiment is the same as the structure of the compressor to the same as the label, detailed description is omitted.

In Figure 9 in, a discharge passage through the cylinder hole 33 of the inner wall 33b of the ring 33a forming the step, is connected to the oil reservoir chamber 47 (with reference to Figure 1) the fairway 39 in the ring 33a opening near difference department of the structure and section 1 of the embodiment is the same as the compressor. Cover 85 and the section 6 of the compressor of the embodiment is equally through the iron plate stamping the formed sheet, but can be through other material and processing method thereof is formed. The cover 85 is formed with a bottom cylindrical, with large-diameter flange portion 85a, and with the inner wall surface 33b of the inner diameter of the outer diameter of the same ring 85b.

By respectively the cover 85 of the flange part 85a pressed into the separation chamber 83 of the ring 33a in, will win 85b into the separation chamber 83 the inner wall 33b and is fixed, in the outer ring 85b with the outer peripheral surface of the expanded diameter hole 33b is formed between the inner peripheral surface of the annular space 86. Furthermore, the cover 85 at the lower part of the (Figure 9 the lower part of the), in the flange portion 85a and the outer ring 85b on the longitudinal walls, is provided with a throttling passage 87, throttle passage 87 will separation chamber 83 and the annular space 86 is connected. The annular space 86 is communicated with the separation chamber as 83 play a function of the oil storage unit.

In paragraph 7 embodiment, discharge chamber 26 through the high-pressure coolant gas lead-in passage 40 is supplied to the oil separator 35 the cylinder part 35a in, through one side of the wound around the same to the cover 85 and the oil side of the centrifugal separation of the transfer. The oil separated from the flow of the coolant gas with paragraph 1 embodiment and 6 the same embodiment.

The oil separated from the coolant gas of the cooling medium gas by G the role of the twisted stream, in the outer ring 85b to rotate and a part of the inner surrounding of falls in the dead weight, is easy to accumulate in the outer ring 85b the lower part of the of the (Figure 8 below). Accumulated in ring 85b G of the lower part of the oil via the throttle passage 87 flows into the annular space 86 in, and then under the action of the pressure difference from the annular space 86 through the by-pass oil passage 39 to the oil reservoir chamber 47 (with reference to Figure 1) is discharged. Therefore, section 7 of the compressor of the embodiment can play paragraph 1 embodiment and 6 the advantages of the compressor of the embodiment of the combination of the advantages of superposition.

Figure 10 shown in section 8 of the embodiment of the change of the compressor section 1 the structure of the embodiment, therefore, to the section 1 of the embodiment is the same as the structure of the compressor to the same as the label, detailed description is omitted.

In section 8 in the compressor of the embodiment, oil separator 90 is integrally formed in the rear housing part 14 on.

In Figure 10 in, along the axis of the drive shaft of the compressor extending in the direction of the discharge passage 88 of the inner wall 89 in the axial direction has a certain diameter. A cylindrical oil separator 90 projecting into the discharge passage 88 the mainland integrally formed in the rear housing part 14 on. A rear housing member 14 is provided with the separation chamber 42 and the high pressure fluid chamber 44 communicated with the discharge passage 91, the discharge passage 91 by V-shaped bending of the through hole is formed. The discharge passage 91 has along the oil separator 90 from the oil separator the axis of the 90 towards the rear at the front end of the housing part 14 of the rear part of the pipe line extending horizontally 90b, and from this pipe line 90b towards the rear shell part 14 extending part of the upper inclined direction. Line 90b with the oil separator 90 on the front end of the inlet opening 90a. Furthermore, the inner wall 89 of the upper (Figure 10 above of) the opening of a throttling function of an appropriate fairway 39.

In the discharge passage 88 of the inner wall 89 and is fixed by pressing in on a plate-shaped cover 92. Cover 92 is set to the disposition position of, the inner end face thereof with the oil passage 39 with the opening. Cover 92 and the oil separator 90 is formed as the space between the separation chamber 93, and is formed with a cover 92 and the inner end face of the inner wall 89 of the oil storage unit 94. The oil storage part 94 is communicated with the separation chamber as 93 play a function of the oil storage unit. Furthermore, in the section 1 shown in the mode of execution of the check valve 36 provided in the discharge passage 91 or external coolant loop 48 in the appropriate position on the path.

In section 8 embodiment, discharge chamber 26 of the high-pressure refrigerant gas is from the lead-in passage 40 is supplied to the oil separator 90 of the outer circumferential surface, on one side of to the cover 92 in the direction of the spiral wound one side of the oil in the process of transferring the centrifugal separation. The oil separated from the coolant gas inlet 90a through line 90b and the discharge passage 91 to the external refrigerant circuit by 48 discharge. In the oil storage part 94 in the upper part of the oil present in the encircled G under the action of the pressure difference from the oil passage 39 to the oil reservoir chamber 47 is discharged.

Paragraph 8 embodiment of a compressor in addition to the section 1 of the embodiment other than the advantages of the compressor, also can be used for forming a substantial reduction of the oil separating device for a number of parts and assembling man-hour, the advantages of the simplified structure.

Figure 11 and Figure 12 is shown in section 9 of the compressor to change the mode of execution of the section 1 of the embodiment a portion of the structure of the compressor, therefore, the structure of the compressor to the same as the same label, detailed description is omitted. In section 1 in the compressor of the embodiment, the cylindrical hole 33 formed in the used to form the throttle passage 38 in increments of 33c, oil passage 39 is communicated with the face cover 34 in the side surface of the annular space, and section 9 of a mode of execution with from the oil reservoir chamber of the compressor 47 to a low-pressure region of the suction chamber 25 of the oil circulation path of the oil.

In Figure 11 in, cylinder hole 33 of the inner wall 33b in the axial direction has a certain diameter, the discharge chamber 26 in an opening. Cover 95 cylinder hole by the corresponding to 33 the diameter of the form of cylindrical metal part, the cover 95 perimeteric surface 95a is, as shown in Figure 12 as formed with an annular groove 96. Groove 96 form as the oil circulation path 97 oil of a part of the intermediate passage 100, oil circulation path is equivalent to 97 throttle portion in the oil. Groove 96 through the lathe cutting processing or press punching processing and easily forming. Cover 95 through the press is fixed to the cylinder hole 33 in, divided separation chamber 42. In the fixed covered 95 under the state of, formed by grooves 96 and separation chamber 42 of the inner wall 33b in the middle surrounded by the closed oil passage 100.

Oil circulation path 97 including the grooves 96 and inner wall 33b formed in the middle of the closed oil passage 100, the oil reservoir chamber 47 is communicated with the groove 96 of the oil an upstream passage 98, and a trough 96 is communicated with the suction chamber 25 of the oil downstream passage 99. In Figure 11 only in a part of said, oil, however, an upstream passage 98 and the oil downstream passage 99 formed in the rear housing member 14 is. Oil an upstream passage 98 and the oil downstream passage 99 of the oil set to be less than the cross-sectional area of the intermediate passage 100 the cross-sectional area is large. Therefore, oil intermediate passage 100 for the oil circulation path 97 function of the oil throttling part. Due to the throttling effect of the throttle as oil by grooves 96 to the passage cross-sectional area, therefore, groove 96 according to the cross-sectional area of the passage to determine the performance of the compressor. Furthermore, oil an upstream passage 98 and the oil downstream passage 99 of the passage cross-sectional area can also be produced according to the state of technology to set on. Through the oil circulation path 97 in the middle of the oil in the oil path 100 in the cover groove 96 of the inner wall 33b flow.

The following, has a section 9 the advantages of the embodiment.

(1) is provided with a from the oil reservoir chamber 47 to the suction chamber 25 of the oil circulation path of the oil 97, but also can be only through the cover 95 perimeteric surface 95a process the trough 96 and simply formed as a oil circulation path 97 oil of a part of the intermediate passage 100. Can be formed through cover 95 of the oil circulation path 97. Furthermore, oil circulation path 97 processing becomes easy.

(2) oil throttle portion decision through its throttling effect from the oil reservoir chamber 47 to the suction chamber 25 of the amount of supply of the oil, through the oil throttle section can prevent the refrigerant gas from the oil reservoir chamber 47 to the suction chamber 25 through the.

(3) because the oil in the middle to form a throttle portion in the oil path 100 in, therefore, the intermediate passage 100 should be relatively easy to form and can be easily form an oil throttling part. The formation of path even if the smaller sectional area of the oil throttle under the condition of oil is easy to set the precision of the throttle portion.

(4) since the oil intermediate passage 100 is a trough 96, so the oil intermediate passage 100 equivalent to the oil throttle, oil can be high-precision setting the passage sectional area of the throttle portion. Formed along the inner wall 33b of the oil throttle, it is possible to fully ensure that the oil circulation path 97 the distance of the throttle in the oil.

Figure 13 shown in the section 10 of the embodiment changes the compressor section 9 of the compressor of the embodiment, and the structure of the oil passage in the middle, to the section 1 embodiment and 9 is the same as the embodiment of the structure of the compressor of the same label to omit detailed description.

As shown in Figure 13, the embodiment of the cover of the compressor 101 are pressed into the cylinder hole 33 in, but the cover 101 the peripheral surface 101a of the groove is not formed. In the separation chamber 42 of the inner wall 33b of the outer circumferential surface in 101a is formed on the part of contact with an annular groove 102. In other words, an annular groove 102 formed in the rear housing member 14 is. Groove 102 form as the oil circulation path 97 oil of a part of the intermediate passage 100, oil circulation path is equivalent to 97 throttle portion in the oil. Groove 102 can be formed by lathe processing easily formed through cutting. In the fixed with a cover 101 under the state of, formed by groove 102 and the cover 101 perimeteric surface 101a surrounded by the closed oil intermediate passage 100.

Oil circulation path 97 comprises an oil intermediate passage 100, the oil reservoir chamber 47 is communicated with the groove 102 of the oil an upstream passage 98, and a trough 102 to the low pressure region is communicated with the suction chamber 25 of the oil downstream passage 99. Oil an upstream passage 98 and the oil downstream passage 99 in Figure 13 only in a part of said. Groove 102 compared to oil the passage-sectional area of an upstream passage 98 and the oil downstream passage 99 of the passage cross-sectional area is small. Oil intermediate passage 100 for the oil circulation path 97 in the oil function throttle portion. Through the oil circulation path 97 in the middle of the oil in the oil path 100 in the covers the groove 102 of the cover 101 perimeteric surface 101a flow.

Section 10 of the embodiment with the compressor 9 the advantages of the compressor of the embodiment (2), (3) the advantages of the same. Furthermore, provided with a from the oil reservoir chamber 47 to the suction chamber 25 of the oil circulation path of the oil 97, but only through the inner wall 33b process the trough 102 can be in the shape of oil intermediate passage 100. And then, the oil is easily formed intermediate passage 100, so the oil circulation path 97 processing becomes easy.

And then, as the throttle portion of the oil in the middle of the oil passage 100 by grooves 102 formed, therefore, can be high-precision setting of oil throttle passage cross-sectional area. Along the outer peripheral surface of the oil throttling part 101a is formed, it is possible to fully ensure that the oil circulation path 97 the distance of the throttle in the oil.

Fig. 14 shows section 11 of the compressor embodiment of the cover 105 of changing the section 9 of the compressor of the embodiment, and the structure of the oil passage in the middle, to the section 1 embodiment and 9 is the same as the embodiment of the structure of the compressor of the same label to omit detailed description.

Figure 14 shows the cover 105 has the radial cross section of the inside of the through hole 106. The through hole 106 is straight, the through hole 106 form as the oil circulation path 97 oil of a part of the intermediate passage 100, oil circulation path is equivalent to 97 shore oil throttle portion of the. Through hole 106 respectively the two ends of the disposed in the opening of the cover 105 perimeteric surface 105a is, corresponding to the two openings in the inner wall 33b of the oil an upstream passage 98 and the oil downstream passage 99 on the position of the opening of the position of the. Therefore, when the cover 105 into the cylinder hole 33 is, in the through hole 106 with the oil the orientation of an upstream passage 98 and the oil downstream passage 99 after the consistent opening position of the cover 105 into the cylinder hole 33 in. Furthermore, the through-hole 106 for example, through the drilling processing easily formed.

Through hole 106 compared to oil the passage-sectional area of an upstream passage 98 and the oil downstream passage 99 of the passage cross-sectional area is small. This is in order to make the through hole 106, as oil circulation path 97 function of the oil throttling part. Through the oil circulation path 97 in the middle of the oil in the oil path 100 in the through hole 106 of the flow.

Section 11 of the embodiment with the compressor 9 the advantages of the compressor of the embodiment (2), (3) the advantages of the same. Furthermore, provided with a from the oil reservoir chamber 47 of the low-pressure region to the suction chamber 25 of the oil circulation path of the oil 97, but only through the cover 105 is processed through hole 106 can be in the shape of oil intermediate passage 100. Therefore, oil circulation path 97 processing becomes easy.

Furthermore, as the throttle portion of the oil in the middle of the oil passage 100 from the through-hole 106 formed, therefore, can be high-precision setting of oil throttle passage cross-sectional area. Because of having passed through the cover 105 of the oil inside of the throttle portion, and the cover 105 perimeteric surface 105a is formed on the throttle compared with the case of oil, can be more firmly sustained through the cover 105 relative to the rear housing member 14 of fixed of press. Furthermore, the oil circulation path 97 is not easy to the oil in to the separation chamber 72 or discharge chamber 25 leakage.

Furthermore, in accordance with Figure 15 (a) and 15 (b) to the section 9-section 11 of the embodiment to explain the deformation example of the compressor. In order to facilitate the description, to the section 1 embodiment and section 9 in the same manner as to the implementation of the structure of the same grade, detailed description is omitted. Figure 15 (a) is shown in the cover 110 has a cylindrical ring 111, the outputs 111, for example, by stamping and forming the metal plate. The outputs 111 middle part in the axial direction, is formed with the radial centre of the small diameter section, corresponding to the outputs of the small diameter portion 111 is formed on the outer circumferential surface of the groove 112. The cover 110 are pressed into the cylinder hole 33 in a state, when the airtight form the trough 12 with the oil in an upstream passage 98 and the oil downstream passage 99 the position of the line of the oil circulation path 97.

Figure 15 (b) the cover shown in 115 relative to cylinder hole 33 is not through the press, it is fixed by a snap spring. cylinder hole 33 corresponding to the cover 115 of the diameter of the large diameter section 331, and compared to lid 115 of the small diameter of the small diameter section 332, the large diameter section 331 the small diameter portion 332 a is formed between the step 333. Cover 115 is a cylindrical, the cover 115 perimeteric surface 115a forming two axial sides of the sealing grooves 117, in the sealing grooves 117 between, is formed with, as oil intermediate passage 100 of grooves 116.

On the other hand, the large diameter section 331 of the inner wall surface 331a the circlip uses is formed near the opening of the annular groove 334. A seal member 118 is mounted on the cap 115 of the sealing grooves 117 in, the cover 115 is inserted into the large diameter section 331 in, until the bumps arrives to step 333. And, through the circlip 119 is installed in the annular groove 334 in, preventing cover 115 from the cylinder hole 33 from falling off. A sealing member 118, oil circulation path 97 almost not to the oil separation chamber 42 and discharge chamber 26 from leaking.

Furthermore, in accordance with Figure 16 and Figure 17 the other an example for description. Figure 16 shows the article 1 with other example 1 embodiment and 9 of the embodiment partially applicable to the structure of the compressor. To the section 1 and 9 of the embodiment is the same as the structure of the compressor common to mark, detailed description is omitted. In the paragraph 1 other embodiment, the cylindrical hole 33 formed in the throttling path to form useful 38 step of 33c, oil passage 39 is communicated with the face cover 120 of the outer peripheral surface of the annular space, in addition is provided with a from the oil reservoir chamber 47 to a low-pressure region of the suction chamber 25 of the oil circulation path of the oil 97.

The cylinder hole 33 of the film (in fig. 16 is the left), than with cylinder hole 33 the diameter of the large diameter of the ring 33a. In in the punches, install the discharge chamber 26 and by cylinder hole 33 is separated from the discharge passage formed in the cover 120. Cover 120 is provided with a flange portion 120a and win 120b, the cover 120 perimeteric surface 120c is, through the flange portion 120a and win 120b difference department are formed. Cover 120 through the win 120b is embedded in the cylinder hole 33 of the inner wall 33b is, the flange portion 120a is embedded in the ring 33a is fixed to the cylinder hole in the 33 upper. The win 120b and ring 33a form the annular space 37. In corresponding to the flange portion 120a of cover 120 perimeteric surface 120c is formed with an annular groove 121. Trough 121 form as the oil circulation path 97 oil of a part of the intermediate passage 100, corresponding to the oil circulation path 97 throttle portion in the oil.

In the fixed covered 120 under the state of, formed by grooves 121 and ring 33a surrounded the inner wall of the closed oil intermediate passage 100. Oil circulation path 97 including the grooves 121 and the inner wall surface of the airtight form of oil intermediate passage 100, will the oil reservoir chamber 47 and the groove 121 of the oil is communicated with an upstream passage 98, and the groove 121 and a low-pressure area of the oil suction chamber is communicated with the downstream passage 99. According to the paragraph 1 other example, the separate and discharges the coolant gas accumulated in the separation chamber 42 G the bottom part of the oil through the throttling passage 38 to the annular space 37 flows in the direction of, and then through fairway 39 to the oil reservoir chamber 47 supply. The oil reservoir chamber 47 of the oil through the oil circulation path 97 to the suction chamber 25 is supplied.

Furthermore, to fig. 17 shown in the section of the 2 other an example for description. Section 2 other embodiment and 2 embodiment and 9 of the embodiment partially applicable to the structure of the compressor. To the section 2 and 9 of the embodiment is the same as the structure of the compressor common to mark, detailed description is omitted. In the paragraph 2 other embodiment, as shown in Figure 17, the cover 125 is formed with a throttling passage 127, in addition to the oil passage 39 is communicated with the face cover 125 perimeteric surface 125c of the annular space 37 outside, is also provided with a from the oil reservoir chamber 47 to a low-pressure region of the suction chamber 25 of the oil circulation path of the oil 97.

The cylinder hole 33 of the film (in fig. 17 is the left), than with cylinder hole 33 the diameter of the large diameter of the ring 33a. Cover 125as shown in Figure 17, is provided with a flange part 125a and win 125b, the cover 125 perimeteric surface 125c is, through the flange portion 125a and win 125b forming difference department. Cover 125 outputs of 125b is fixed to the cylinder hole 33 is. In corresponding to the flange portion 125a perimeteric surface 125c is formed with an annular groove 126. Groove 126 form as the oil circulation path 97 oil of a part of the intermediate passage 100, oil circulation path is equivalent to 97 of the oil throttling part.

The embodiment of the throttling path 127 by the cover 125 outputs of 125b along the deepest position and perpendicular to the cover 125 in a direction perpendicular to the axis of the (in fig. 17 is in the direction of the) extending through hole 128 is formed. This throttling passage 127 of the separation chamber 42 is communicated with the annular space 37. Therefore, the separate and discharges the coolant gas accumulated in the separation chamber 42 the oil on the bottom portion through the throttling path G 127 to the annular space 37 flows in the direction of, and then through fairway 39 is supplied to the oil reservoir chamber. The oil reservoir chamber through the oil circulation path of the oil 97 is supplied to the suction chamber.

Furthermore, the invention is not limited to the above-mentioned embodiment, the main purpose of the invention to various changes within the range of, for example, can be as the following such a change.

In paragraph can also be 1-8 embodiment the discharge passage is disposed, relative to the axial direction of the compressor extending inclined, in this discharge passage matches supposes the oil separator.

Section 1-4 of the embodiment of the cover can also be such as paragraph 5-section 8, as described in the embodiment by pressing in and fixed in the round hole.

In section 3 and 5 embodiment, can also be the base 64, 76 through the press-fit fixing the cylinder hole 33 in, the cover 62, 74 is arranged on the outer peripheral surface of the sealing member. Such a structure makes the part 61, 73 of the assembly becomes easy. Furthermore, the sealing member is not limited to 62, 74 of the outer circumferential surface, can be provided with a formed on the cylinder hole 33 of the inner wall 33b of the cover difference department 62, 74 between the end face of the.

In section 1-8 embodiment, oil passage 39 may be provided on the lower part of the oil storage unit. If the thus constituted, is accumulated in the lower part of the by self-weight of the oil can be discharged.

In section 1-8 embodiment, is arranged on the upper part of the oil in the separating chamber, but can be disposed in the separation chamber of the oil reservoir chamber or below the horizontal position of the most appropriate.

In section 1-5 embodiment and 7 embodiment, and can also be a discharge passage formed in the inner wall surface of the circular hole, the outer peripheral surface of the cover or on the step of the two forms the taper.

Section 1 and 5 of the embodiment of the gas passage hole 63a, 75c with respect to the line 65, 77 extending right angle to the central axis, but as long as they are in a direction crossing with the central axis, can also be other than relative to the central axis at right angles to the angle. Furthermore, the gas passage hole 63a, 75c in 4 parts of the structure of the on, but can be disposed in the 4 position on a plurality of positions outside.

In section 1-4 embodiment and 7 embodiment, it is formed on the lid of a perimeter of the shape of the cross section of the annular space is a quadrangle, but is not limited to this, also can be the cross-section triangle, can also be of circular cross-section, can also be a cross-sectional elliptical shape. In short, as long as they can make the oil through the, annular space is how can the cross-sectional shape.

In section 1, paragraph 3 and 4 embodiment, through the in the separating chamber arranged on the inner wall surface of the step formed at the lower part of the cover of the throttle path, but also can be through the ring of the cover is provided with the step to form a throttle passage.

In section 8 embodiment, the cover can also be through 92 thickensed, or on the cover 92 is provided with a flange part, the cover 92 and a part of the oil passage 39 of the opening. Therefore, can reduce the oil passage 39 the opening, increasing the throttling effect.

In section 9-11 embodiment and its deformation embodiment, in order to become simple and throttle portion causes the oil the oil circulation path in the oil passage in the middle function as oil throttle portion, but the oil intermediate channels may also be not necessarily function as oil throttle portion, oil throttling channels may also be in the oil circulation path of freely setting the midway. For example, the oil can also be an upstream passage and downstream passage is arranged in the oil of the oil throttling part.

In subsection 1-11 embodiment, a compressor is a variable-capacity inclined-plate compressor is described, but the compressor can also be a fixed displacement, can also be a swing type. Furthermore, the compressor is not limited to swash plate type, vane type or whorl can also be rotary and the like.