KR102027178B1

KR102027178B1 - Double-headed swash plate type compressor

Info

Publication number: KR102027178B1
Application number: KR1020140043541A
Authority: KR
Inventors: 김민규
Original assignee: 한온시스템 주식회사
Priority date: 2014-04-11
Filing date: 2014-04-11
Publication date: 2019-11-04
Also published as: KR20150117872A

Abstract

The present invention relates to a two-head swash plate type compressor in which a suction refrigerant introduced into a rotating shaft flows into a cylinder bore and is compressed. According to one embodiment of the present invention, a cylinder protrusion and a radial are respectively disposed at both sides by a refrigerant introduction of a cylinder block. A rotating shaft is supported by the bearing, and an oil film is formed around the rotating shaft by the oil pocket, thereby providing a double head swash plate type compressor which minimizes wear and oil leakage around the rotating shaft.

Description

Double-headed swash plate type compressor

The present invention relates to a double head swash plate compressor, and more particularly, to a double head swash plate compressor in which the suction refrigerant introduced into the rotating shaft flows into the cylinder bore and is compressed.

In general, a vehicle air conditioner is a device that maintains a temperature inside a car lower than an outside temperature by using a refrigerant, and includes a compressor, a condenser, and an evaporator to configure a circulation cycle of the refrigerant.

At this time, the compressor is a device that compresses and pumps the refrigerant, and is operated by the power of the engine or the driving of the motor.

In the two-head swash plate compressor, which is a kind of reciprocating compressor, a disk-shaped swash plate is installed on a rotating shaft that receives power of an engine. A plurality of pistons are installed along the circumference of the swash plate via a shoe, and when the swash plate rotates, the plurality of pistons suck and compress the refrigerant by reciprocating linearly in the plurality of cylinder bores formed in the cylinder block. At this time, a valve plate intermittent between the housing and the cylinder block to intake and discharge the refrigerant.

1 is an example of a conventional two-head swash plate type compressor, which is disclosed in Korean Patent No. 10-0554553.

In the case of the double-head swash plate compressor 10 shown in FIG. 1, the front housing 20 and the rear housing 30 are respectively coupled to the cylinder block 40, and the discharge chamber 21 is formed in the front housing 20. The discharge chamber 31 and the suction chamber 32 are respectively formed in the rear housing 30.

The rotating shaft 50 is rotatably supported by the cylinder block 40 and passes through the through hole 41 of the cylinder block 40. At this time, the rotation shaft 50 is directly supported by the cylinder block 40 at the position of the through hole 41.

Each through hole 41 extends with a different radius along the longitudinal direction of the rotation shaft 50, and a seal surface 42 is formed in contact with the rotation shaft 50 at the smallest radius of the through hole 41. do. That is, the rotation shaft 50 is directly supported by the cylinder block 40 on the seal surface 42.

A passage 51 is formed in the rotational shaft 50 along the longitudinal direction, and one end thereof communicates with the suction chamber 32. An introduction passage 52 is formed on the outer circumferential surface of the rotation shaft 50 so as to communicate with the passage 51.

A suction passage 44 is formed in the cylinder block 40 so that the cylinder bore 43 communicates with the through hole 41, and the inlet of the suction passage 44 is opened on the seal surface 42.

At this time, the end of the introduction passage 52 is in intermittent communication with the inlet of the suction passage 44 in accordance with the rotation of the rotary shaft (50).

However, in the two-head swash plate type compressor 10 described above, the outer circumferential surface of the rotating shaft 50 excessively contacts the inner circumferential surface of the cylinder block 40, so that the outer circumferential surface or the cylinder of the rotating shaft 50 when the rotating shaft 50 rotates. Wear is likely to occur on the inner circumferential surface of the block 40.

In addition, a gap is formed between the outer circumferential surface of the rotating shaft 50 and the inner circumferential surface of the cylinder block 40 in order to rotate the rotating shaft 50, and leakage of the refrigerant through the gap is inevitable. If there is a problem that the leakage amount soared, there is a problem that causes the efficiency of the compressor (10).

KR 10-0554553 B1 (2006.02.16 Enrollment)

The present invention has been made to solve the above problems, to provide a two-head swash plate compressor that can minimize the occurrence of wear with the cylinder block due to the rotation of the rotation shaft, and prevent or minimize the leakage of refrigerant to the periphery of the rotation shaft For the purpose.

According to a preferred embodiment of the present invention, the center bore is formed in the center, a plurality of cylinder bores are formed in the circumferential direction spaced apart from each other in the radially outer direction of the center bore, the center bore and the cylinder bore communicating A cylinder block in which a refrigerant introduction passage is formed; A front housing and a rear housing which are respectively coupled to the front and rear of the cylinder block to form a discharge chamber; A rotating shaft mounted to the center bore of the cylinder block through the front housing and having a coolant flow path formed therein in a longitudinal direction, and having a coolant inflow hole and a coolant discharge hole communicated with the coolant flow path on an outer circumferential surface thereof; And compression means for compressing the working fluid in the cylinder bore and discharging it into the discharge chamber according to the rotation of the rotary shaft, wherein a radial bearing rotatably supporting the rotary shaft is mounted on one side of the inner circumferential surface of the center bore.
An annular oil pocket 232 is formed in the radial direction between the radial bearing 800 and the cylinder block 200 based on the rotation shaft 500, and the rotation shaft 500 when the rotation shaft 500 is rotated. Oil flowing along the outer circumferential surface of the air is filled in the oil pocket 232, and an oil film 233 is formed between the rotary shaft 500 and the cylinder block 200 in the axial direction and the radial direction to form the rotary shaft 500. At the same time as preventing the leakage of the refrigerant along the outer circumferential surface of the rotating shaft 500, the radial bearing 800 is thermally expanded to the rotating shaft 500 and the outer circumferential surface of the rotating shaft 500 and the radial bearing ( The interval t2 between the inner circumferential surface of the 800 is provided with a double-head swash plate type compressor, characterized in that the interval smaller than the interval t1 between the outer circumferential surface of the rotation shaft 500 and the inner circumferential surface of the center bore 230 is maintained.

Here, the rotating shaft is supported by the radial projection and the cylinder protrusion which is formed to protrude forward and backward along the center bore rim of the cylinder block, respectively.

At this time, the cylinder protrusion and the radial bearing are respectively disposed on both sides by the refrigerant introduction of the cylinder block along the longitudinal direction of the rotating shaft.

In addition, the radial bearing is formed by joining dissimilar metals having different thermal expansion coefficients.

In this case, the radial bearing includes an inner member facing the rotating shaft and an outer member facing the cylinder block, and at least one of the inner member and the outer member is made of a material different from that of the cylinder block.

In this case, the inner member may be an aluminum alloy material, and the outer member may be a steel alloy material.

In addition, the inner member may contain 5.0% to 7.5% of tin (Sn).

In addition, a radial bearing seating groove is formed along the circumferential direction on one side of the inner circumferential surface of the center bore to be spaced apart from the refrigerant introduction passage.

In addition, the radial bearing is mounted on one side of the radial bearing seating groove.

At this time, the inner diameter of the radial bearing is preferably the same as the inner diameter of the center bore.

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According to the two-head swash plate type compressor according to the preferred embodiment of the present invention, a radial bearing seating groove is formed on one side of the inner circumferential surface of the center bore, and an oil film is formed in the gap between the rotating shaft and the center bore by oil introduced into the radial bearing seating groove. Therefore, there is an effect of preventing or minimizing refrigerant leakage to the periphery of the rotating shaft as in the prior art.

In addition, since the radial bearing rotatably supporting the rotating shaft is mounted on one side of the inner circumferential surface of the center bore, there is an effect of minimizing wear caused by the load concentrated on the contact portion of the rotating shaft and the center bore when the rotating shaft rotates.

In addition, since the inner member of the radial bearing is formed of a material that is advantageous for the rotational sliding of the rotating shaft, the wear caused by the friction is minimized.

In addition, since the radial bearing is formed by joining dissimilar metals having different thermal expansion coefficients, the gap between the rotating shaft and the center bore changes when the temperature rises during the operation of the compressor, so that the rotating shaft is firmly supported.

1 is a cross-sectional view of a conventional double-head swash plate compressor.
Figure 2 is a cross-sectional view of a two-head swash plate compressor according to an embodiment of the present invention.
3 is a cross-sectional view taken along the line AA of FIG.
Figure 4 is a schematic diagram showing a support structure of a rotating shaft according to an embodiment of the present invention.
Figure 5 is a schematic diagram showing a state in which a radial bearing is mounted on a rotating shaft according to an embodiment of the present invention.
6 is a schematic view showing a state in which the inner member of the radial bearing is thermally expanded during the rotation of the rotary shaft according to an embodiment of the present invention.

Hereinafter, with reference to the accompanying drawings, a preferred embodiment of the present invention double head swash plate compressor will be described. In this process, the thickness of the lines or the size of the components shown in the drawings may be exaggerated for clarity and convenience of description.

In addition, terms to be described below are terms defined in consideration of functions in the present invention, which may vary according to the intention or convention of a user or an operator. Therefore, definitions of these terms should be made based on the contents throughout the specification.

In addition, the following embodiments are not intended to limit the scope of the present invention but merely illustrative of the components set forth in the claims of the present invention, which are included in the technical spirit throughout the specification of the present invention and constitute the claims Embodiments that include a substitutable component as an equivalent in the element may be included in the scope of the present invention.

Example

2 is a cross-sectional view of a double-head swash plate compressor according to an embodiment of the present invention, Figure 3 is a cross-sectional view taken along the line A-A of FIG. The thick dashed-dotted arrow shown in FIG. 2 indicates the flow direction of the refrigerant.

As shown in FIG. 2, a double head swash plate compressor (hereinafter, referred to as a 'compressor') 100 according to an embodiment of the present invention includes a cylinder block in which a center bore 230 and a plurality of cylinder bores 240 are formed. 200, the front housing 300 and the rear housing 400 coupled to the front and rear of the cylinder block 200, the rotating shaft 500 installed through the front housing 300 and the cylinder block 200, And compression means 600 for compressing the working fluid in the cylinder bore 240 according to the rotation of the rotary shaft 500.

The cylinder block 200 includes a front cylinder block 210 and a rear cylinder block 220 which are disposed forward and backward by coupling. The center bore 230 is formed at the inner center of the front cylinder block 210 and the rear cylinder block 220 so as to be equipped with a rotating shaft 500 to be described later, and each other along the circumferential direction on the radially outer side of the center bore 230. A plurality of cylinder bores 240 are spaced apart.

2 and 3, the center bore 230 and the cylinder bore 240 communicate with each other by the coolant introduction path 250, and the coolant flow path 510 of the rotating shaft 500 to be described later. The introduced refrigerant is introduced into each cylinder bore 240 through the refrigerant introduction path 250.

2, the front housing 300 is coupled to the front of the front cylinder block 210. A discharge chamber 310 is recessed in one side of the rear side of the front housing 300, and a valve plate 700 is interposed between the front housing 300 and the front cylinder block 210. In this case, a discharge hole 710 is formed through the valve plate 700 so that the cylinder bore 240 of the front cylinder block 210 and the discharge chamber 310 of the front housing 300 communicate with each other. One side of the discharge chamber 310 side is provided with a discharge valve 720 for opening and closing the discharge hole 710.

The rear housing 400 is coupled to the rear of the rear cylinder block 220. A discharge chamber 410 is recessed in one front side of the rear housing 400, and a valve plate 700 is interposed between the rear housing 400 and the rear cylinder block 220. At this time, the discharge hole 710 is formed through the valve plate 700 so that the cylinder bore 240 of the rear cylinder block 220 and the discharge chamber 410 of the rear housing 400 communicate with each other. One side of the discharge valve 720 for opening and closing the discharge hole 710 is provided.

The front housing 300 and the front cylinder block 210, the rear cylinder block 220, and the rear housing 400 are combined by fasteners such as bolts to form an overall appearance of the compressor 100.

On the other hand, a rotating shaft 500 for transmitting the rotational force of the engine through the front housing 300, the front cylinder block 210 and the rear cylinder block 220 is rotatably installed. The rotary shaft 500 is mounted to the center bore 230 of the front cylinder block 210 and the rear cylinder block 220 through the shaft hole 320 formed in the center of the front housing 300.

At this time, the cylinder protrusion 211 protrudes forward along the edge of the center bore 230 of the front cylinder block 210, the cylinder protrusion 221 to the rear along the edge of the center bore 230 of the rear cylinder block 220. ) Is formed to protrude. The cylinder protrusions 211 and 221 serve to support the rotating shaft 500 together with the radial bearing 800 to be described later.

A refrigerant passage 510 is formed in the rotation shaft 500 along a length direction, and a refrigerant inlet hole 520 and a refrigerant discharge hole 530 are formed through the outer circumferential surface thereof so as to communicate with the refrigerant passage 510. At this time, the refrigerant inlet hole 520 is formed at one side of the central portion in the longitudinal direction of the rotation shaft 500. The coolant discharge hole 530 may be formed to be spaced apart from the front and rear of the coolant inlet hole 520 so as to correspond to the coolant introduction path 250 described above. The coolant inlet hole 520 and the coolant discharge hole 530 form a predetermined angle with respect to the central axis of the rotation shaft 500.

The refrigerant is sucked into the cylinder block 200 through a suction port (not shown) provided at one side of the outer circumferential surface of the cylinder block 200, and the refrigerant passage 510 inside the rotating shaft 500 through the refrigerant inlet hole 520. Flows into.

The refrigerant introduced into the refrigerant passage 510 of the rotation shaft 500 is a cylinder bore through the refrigerant introduction passage 250 as the refrigerant discharge hole 530 communicates with the refrigerant introduction passage 250 when the rotation shaft 500 rotates. Flow to 240. The refrigerant introduced into the cylinder bore 240 is compressed by the compression means 600, and the refrigerant compressed at high pressure is discharged to the discharge chambers 310 and 410 through the discharge holes 710. Thereafter, the high pressure refrigerant of the discharge chambers 310 and 410 is supplied to the outside through a discharge port (not shown) provided in the front housing 300 or the rear housing 400.

Here, the compression means 600 according to an embodiment of the present invention, the swash plate 610 is installed to have a predetermined inclination angle on the rotation shaft 500, the cylinder bore 240 in accordance with the rotation of the swash plate 610 It includes a plurality of pistons 620 for linear reciprocating motion.

The swash plate 610 is a means for converting the rotational driving force of the rotary shaft 500 into a linear reciprocating motion of the piston 620, and inclined to one side of the hub 630 coupled to penetrate the central portion on the rotary shaft 500. Is installed, the swash plate 610 with the hub 630 rotates integrally when the rotary shaft 500 rotates. A coolant inlet 631 is formed through one side of the outer circumferential surface of the hub 630, and the coolant inlet 631 communicates with the coolant inlet hole 520 of the rotation shaft 500. On the other hand, a plurality of shoes 611 are provided along the circumferential direction at the edge portion of the swash plate 610, and the plurality of pistons 620 are slidably supported by the shoe 611 so as to be relatively movable.

At this time, since the swash plate 610 is moved forward and backward while rotating in the inclined state, the swash plate 610 is moved to the left and right by the axial load to the swash plate 610 or the hub 630 or the rotating shaft ( 500) may be deformed.

To prevent this, thrust bearings 540 are interposed between both sides of the hub 630 and the front and rear cylinder blocks 210 and 220, respectively. The thrust bearing 540 protrudes along the edges of both ends of the hub 630 to act as a damping first support protrusion 632 and the hub 630 along the inner edge of the center bore 230 of the front and rear cylinder blocks 210 and 220. It is supported by the second support protrusions (212, 222) protruding respectively in the direction.

A radial bearing seating groove 231 is formed at one side of the inner circumferential surface of the center bore 230 along the circumferential direction. The radial bearing 800 is press-fitted to the radial bearing seating groove 231. The inner diameter of the radial bearing 800 and the center bore 240 so that the inner circumferential surface of the radial bearing 800 mounted in the radial bearing seating groove 231 does not protrude into the center bore 230 when the radial bearing 800 is mounted. It is preferable that the inner diameter of is the same.

The radial bearing 800 is mounted to the center bore 230 of the front cylinder block 210 and the center bore 230 of the rear cylinder block 220, respectively, to rotatably support the rotating shaft 500.

At this time, the radial bearing 800 is a ring-shaped outer member 820 is coupled to the outside of the ring-shaped inner member 810, at least one of the inner member 810 and the outer member 820 is a cylinder block ( 200).

Preferably, the inner member 810 and the outer member 820 have different coefficients of thermal expansion. As an example, the inner member 810 may be made of an aluminum (Al) alloy material, and the outer member 820 may be made of a steel alloy material such as Fe-C.

More preferably, the inner member 810 may be made of an aluminum alloy (Al-Sn) material containing 5.0 to 7.5% of tin (Sn) to favor the sliding slide of the rotating shaft 500. In this case, the cylinder block 200 may be made of an Al-Si alloy material.

Meanwhile, an oil pocket 232 is formed at one side of the radial bearing 800. At this time, as shown in FIG. 2, when the radial bearing 800 is press-fitted into the radial bearing seating groove 231, there is a slight gap between the bottom surface of the radial bearing seating groove 231 and the radial bearing 800. gap) is formed, and the space formed by the gap forms the oil pocket 232.

When the rotary shaft 500 rotates, oil (lubricating oil) flowing along the outer circumferential surface of the rotary shaft 500 is filled in the oil pocket 232, and the oil collected in the oil pocket 232 is cylinder block 200 and the rotary shaft 500. An oil film 233 (see FIG. 5) is formed therebetween.

That is, the clearance gap between the bottom surface of the radial bearing seating groove 231 and one surface of the radial bearing 800 in the radial bearing seating groove 231 forms an oil pocket 232, and is filled in the oil pocket 232. By the oil that is, the oil film 233 is formed between the rotary shaft 500 and the cylinder block 200, it is possible to prevent or minimize the leakage of the refrigerant (leak) generated along the outer peripheral surface of the rotary shaft 500 .

In addition, conventionally, as the outer circumferential surface of the rotating shaft 500 excessively contacts the inner circumferential surface of the center bore 230, wear occurred on the rotating shaft 500 or the cylinder block 200 when the rotating shaft 500 rotates. However, according to the exemplary embodiment of the present invention, since the cylinder protrusions 211 and 221 and the radial bearing 800 support the rotation shaft 500, wear occurrence may be minimized.

Figure 4 is a schematic diagram showing a support structure of a rotating shaft according to an embodiment of the present invention.

The rotary shaft 500 is supported by the cylinder protrusions 211 and 221 and the radial bearing 800, and the cylinder protrusions 211 and 221 and the radial bearing 800 are along the longitudinal direction of the rotary shaft 500. It is disposed at both ends of the refrigerant introduction passage (250).

That is, both sides of the refrigerant introduction passages 250 of the front and rear cylinder blocks 210 and 220 are supported by the cylinder protrusions 211 and 221 and the radial bearing 800, respectively.

At the time of the compression stroke, one side of the outer circumferential surface of the rotating shaft 500 is in close contact with the refrigerant introduction passage 250 to provide a sufficient sealing force through the supporting structure, while the outer circumferential surface of the rotating shaft 500 and the front and rear cylinder blocks ( By minimizing abrasion generated between the inner circumferential surface of the center bore 230 of the 210, 220, it is possible to minimize the leakage of the refrigerant around the rotating shaft (500).

For example, in the compression stroke by the upper piston 620 in FIG. 2, when the piston 620 moves from left to right in the drawing, the refrigerant in the cylinder bore 240 is compressed. At this time, the communication between the refrigerant discharge hole 530 and the refrigerant introduction passage 250 is blocked by the rotation of the rotary shaft 500, and the outer circumferential surface of the rotary shaft 500 comes into close contact with the refrigerant introduction passage 250 and the refrigerant introduction passage 250. Leakage of the refrigerant through) is prevented or minimized.

At this time, according to an embodiment of the present invention, the cylinder protrusions 211 and 221 and the radial bearing 800 supporting the rotating shaft 500 are intensively loaded. Therefore, the load excessively concentrated in a partial region of the outer circumferential surface of the rotating shaft 500 corresponding to the conventional refrigerant introduction path 250 may be distributed to the cylinder protrusions 211 and 221 and the radial bearing 800 to minimize the wear phenomenon.

5 is a schematic view showing a state in which the radial bearing is mounted on the rotating shaft according to an embodiment of the present invention, showing an example in which the radial bearing is mounted on the center bore of the rear cylinder block.

At this time, the inner diameter of the center bore 230 and the inner diameter of the radial bearing 800 is preferably the same, so that the clearance between the outer circumferential surface of the rotary shaft 500 and the inner circumferential surface of the radial bearing 800 is the outer circumferential surface of the rotary shaft 500 and the center bore ( It has the same space t1 as the clearance gap between the inner peripheral surfaces of 230.

A radial bearing seating groove 231 is formed in one side of the inner circumferential surface of the center bore 230 along the circumferential direction, and a radial bearing 800 is mounted on one side of the radial bearing seating groove 231.

When the radial bearing 800 is mounted in the radial bearing seating groove 231, an oil pocket 232 is formed at one side of the radial bearing 800, and the rotary shaft 500 is rotated in the oil pocket 232 when the rotating shaft 500 is rotated. The oil flowing along the outer circumferential surface of the is filled. An oil film 233 is formed between the rotating shaft 500 and the cylinder block 200 by the oil filled in the oil pocket 232, and the oil film 233 prevents the refrigerant from leaking along the outer circumferential surface of the rotating shaft 500. Or to minimize it.

FIG. 6 is a schematic view illustrating a thermal expansion of an inner member of a radial bearing during rotation of a rotating shaft according to an embodiment of the present invention, showing an example in which a radial bearing is mounted on a center bore of a rear cylinder block.

As described above, the radial bearing 800 is made by the combination of the inner member 810 and the outer member 820 having different coefficients of thermal expansion, the thermal expansion coefficient of the inner member 810 is It is larger than the coefficient of thermal expansion.

Therefore, when heat is generated by the rotation of the rotary shaft 500, as shown in FIG. 6, the inner circumferential surface of the inner member 810 expands in the direction of the rotary shaft 500, wherein the outer circumferential surface of the rotary shaft 500 and the radial bearing 800 are rotated. The interval t2 between the inner circumferential surfaces is smaller than the interval t1 between the outer circumferential surface of the rotation shaft 500 and the inner circumferential surface of the center bore 230. That is, when the temperature rises due to the rotation operation of the rotary shaft 500, the inner member 810 of the radial bearing 800 expands into the center bore 230 to more firmly support the rotary shaft 500.

As described above, according to an embodiment of the present invention by the rotary shaft 500 is supported by the cylinder protrusions 211 and 221 and the radial bearing 800, excessive contact between the conventional rotary shaft 500 and the inner circumferential surface of the center bore 230 It is possible to minimize wear caused by.

In addition, by forming an oil pocket 232 on one side of the radial bearing 800 pressed into the radial bearing seating groove 231, an oil film 233 is formed around the rotary shaft 500, the rotary shaft 500 as in the prior art It is possible to prevent or minimize leakage of refrigerant around.

In addition, since the radial bearing 800 is formed by the combination of the inner member 810 and the outer member 820 having different coefficients of thermal expansion, the rotation shaft 500 is more firmly supported when heat is generated by the rotation of the rotary shaft 500. You can do it.

100 compressor 200 cylinder block
210: front cylinder block 220: rear cylinder block
230: center bore 231: radial bearing seating groove
232: oil pocket 240: cylinder bore
250: refrigerant introduction 300: front housing
400: rear housing 500: rotation axis
510: refrigerant passage 520: refrigerant inlet hole
530: refrigerant discharge hole 600: compression means
610: swash plate 620: piston
630 hub 631 refrigerant inlet
700: valve plate 800: radial bearing
810: inner member 820: outer member

Claims

A center bore 230 is formed at the center, and a plurality of cylinder bores 240 are formed to be spaced apart from each other in the circumferential direction on the radially outer side of the center bore 230, and the center bore 230 and the cylinder bore ( A cylinder block 200 in which a refrigerant introduction path 250 communicating with 240 is formed;
A front housing 300 and a rear housing 400 coupled to the front and the rear of the cylinder block 200 to form discharge chambers 310 and 410, respectively;
It is mounted to the center bore 230 of the cylinder block 200 through the front housing 300, the refrigerant passage 510 is formed in the longitudinal direction therein, the outer peripheral surface is in communication with the refrigerant passage 510 A rotating shaft 500 in which a coolant inlet hole 520 and a coolant discharge hole 530 are respectively formed; And
Compression means 600 for compressing the working fluid in the cylinder bore 240 in accordance with the rotation of the rotary shaft 500 to discharge to the discharge chamber (310,410),
The radial bearing 800 rotatably supporting the rotating shaft 500 is mounted on one side of the inner circumferential surface of the center bore 230,
An annular oil pocket 232 is formed in a radial direction between the radial bearing 800 and the cylinder block 200 based on the rotation shaft 500,
When the rotating shaft 500 is rotated, oil flowing along the outer circumferential surface of the rotating shaft 500 is filled in the oil pocket 232,
While forming an oil film 233 in the axial direction and the radial direction between the rotary shaft 500 and the cylinder block 200 to prevent the refrigerant from leaking along the outer peripheral surface of the rotary shaft 500,
When the rotary shaft 500 is rotated, while the radial bearing 800 thermally expands to the rotary shaft 500, a distance t2 between the outer circumferential surface of the rotary shaft 500 and the inner circumferential surface of the radial bearing 800 is determined by the rotation shaft 500. A two-head swash plate type compressor, characterized in that a spacing smaller than the spacing t1 between the outer circumferential surface and the inner circumferential surface of the center bore 230 is maintained.

The method according to claim 1, The rotating shaft 500,
Double head swash plate type compressor, characterized in that supported by the radial bearing (800) and the cylinder projections (211, 221) protruding forward and rearward along the edge of the center bore 230 of the cylinder block (200), respectively.

The method according to claim 2,
The cylinder protrusions 211 and 221 and the radial bearing 800 are double headed swash plate types, which are respectively disposed on both sides of the refrigerant introduction path 250 of the cylinder block 200 along the longitudinal direction of the rotation shaft 500. compressor.

The method of claim 1, wherein the radial bearing 800,
A two-head swash plate type compressor characterized by bonding of dissimilar metals each having a different coefficient of thermal expansion.

The method of claim 4, wherein the radial bearing 800,
An inner member 810 facing the rotating shaft 500 and an outer member 820 facing the cylinder block 200,
At least one of the inner member (810) and the outer member (820) is a two-head swash plate compressor, characterized in that made of a different material from the cylinder block (200).

The method according to claim 5,
The inner member 810 is made of aluminum alloy, the outer member 820 is a two-head swash plate type compressor, characterized in that the steel alloy material.

The method according to claim 6,
The inner member 810 is a bi-swash plate-type compressor, characterized in that containing 5.0% to 7.5% of tin (Sn).

The method according to claim 1,
The two-head swash plate-type compressor, characterized in that the radial bearing seating groove (231) is formed along the circumferential direction on one side of the inner circumferential surface of the center bore (230) spaced apart from the refrigerant introduction path (250).

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The method according to claim 8,
Double head swash plate type compressor, characterized in that the radial bearing 800 is mounted on one side of the radial bearing seating groove (231).

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The method according to claim 10,
Double radial swash plate compressor characterized in that the inner diameter of the radial bearing (800) is the same as the inner diameter of the center bore (230).

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