KR20150117872A - Double-headed swash plate type compressor - Google Patents

Double-headed swash plate type compressor Download PDF

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Publication number
KR20150117872A
KR20150117872A KR1020140043541A KR20140043541A KR20150117872A KR 20150117872 A KR20150117872 A KR 20150117872A KR 1020140043541 A KR1020140043541 A KR 1020140043541A KR 20140043541 A KR20140043541 A KR 20140043541A KR 20150117872 A KR20150117872 A KR 20150117872A
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South Korea
Prior art keywords
radial bearing
cylinder block
rotary shaft
center bore
cylinder
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KR1020140043541A
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Korean (ko)
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KR102027178B1 (en
Inventor
김민규
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한온시스템 주식회사
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Priority to KR1020140043541A priority Critical patent/KR102027178B1/en
Publication of KR20150117872A publication Critical patent/KR20150117872A/en
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Publication of KR102027178B1 publication Critical patent/KR102027178B1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1045—Cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1054—Actuating elements
    • F04B27/1063—Actuating-element bearing means or driving-axis bearing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1054—Actuating elements
    • F04B27/1072—Pivot mechanisms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1081—Casings, housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/109—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/12—Kind or type gaseous, i.e. compressible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2250/00—Geometry
    • F05B2250/40—Movement of component
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

According to an aspect of the present invention, there is provided a double-head swash plate type compressor in which suction refrigerant introduced into a rotary shaft flows into and is compressed by a cylinder bore, A double-head swash plate type compressor is provided in which a rotating shaft is supported by a bearing and an oil film is formed around the rotating shaft by an oil pocket to minimize wear and oil leakage around the rotating shaft.

Description

[0002] A double-headed swash plate type compressor

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a double-head swash plate compressor, and more particularly, to a double-head swash plate compressor in which a suction refrigerant introduced into a rotary shaft flows to a cylinder bore and is compressed.

BACKGROUND ART [0002] Generally, an air conditioner of a vehicle uses a refrigerant to maintain a temperature of a vehicle interior lower than an external temperature, and includes a compressor, a condenser, and an evaporator to form a circulation cycle of the refrigerant.

At this time, the compressor compresses and transports the refrigerant, and is operated by the power of the engine or the driving of the motor.

In a double-head swash plate type compressor, which is a type of reciprocating compressor, a disk-shaped swash plate is installed on a rotary shaft which receives the power of the engine. A plurality of pistons are installed through a shoe along the circumference of the swash plate. When the swash plate is rotated, a plurality of pistons are linearly reciprocated within a plurality of cylinder bores formed in the cylinder block, thereby sucking the refrigerant and discharging the refrigerant. At this time, a valve plate is interposed between the housing and the cylinder block for interrupting suction and discharge of the refrigerant.

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

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. In the case of the double-head swash plate type compressor 10 shown in FIG. And a discharge chamber 31 and a suction chamber 32 are formed in the rear housing 30, respectively.

The rotary 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 rotary shaft 50 is directly supported by the cylinder block 40 at the position of the through-hole 41.

Each of the through holes 41 extends in the radial direction along the longitudinal direction of the rotary shaft 50 and a sealing surface 42 contacting the rotary shaft 50 is formed at a portion where the radius of the through hole 41 is the smallest do. That is, the rotary shaft 50 is directly supported by the cylinder block 40 on the sealing surface 42.

A passage (51) is formed in the rotary shaft (50) along the longitudinal direction, and one end communicates with the suction chamber (32). An introducing passageway (52) is formed in the outer circumferential surface of the rotary 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 intermittently communicates with the inlet of the suction passage 44 in accordance with the rotation of the rotary shaft 50.

The above-described double-head swash plate type compressor 10 is configured such that the outer circumferential surface of the rotary shaft 50 is excessively brought into contact with the inner circumferential surface of the cylinder block 40 so that the outer circumferential surface of the rotary shaft 50, There is a high possibility that the inner peripheral surface of the block 40 is abraded.

In order to rotate the rotary shaft 50, a clearance must be formed between the outer peripheral surface of the rotary shaft 50 and the inner peripheral surface of the cylinder block 40. Leakage of the refrigerant through the clearance is inevitable. There arises a problem that the leakage amount thereof is rapidly increased and the efficiency of the compressor 10 is lowered.

KR 10-0554553 B1 (2006.02.16 Enrollment)

SUMMARY OF THE INVENTION The present invention is conceived to solve the problems as described above, and it is an object of the present invention to provide a double-head swash plate type compressor capable of minimizing occurrence of abrasion with a cylinder block due to rotation of a rotary shaft and preventing or minimizing leakage of refrigerant to a peripheral portion of a rotary shaft .

According to a preferred embodiment of the present invention, a center bore is formed at the center, and a plurality of cylinder bores are formed on the radially outer side of the center bore in a circumferential direction to be spaced apart from each other, and the center bore communicates with the cylinder bore A cylinder block in which a refrigerant introduction path is formed; A front housing and a rear housing coupled to the front and rear sides of the cylinder block to form a discharge chamber; A rotary shaft mounted on the center bore of the cylinder block through the front housing and having a refrigerant passage formed along the longitudinal direction thereof and having a refrigerant inlet hole and a refrigerant discharge hole communicating with the refrigerant passage; And a compression means for compressing the working fluid in the cylinder bore in accordance with the rotation of the rotary shaft and discharging the working fluid to the discharge chamber, wherein a radial bearing for rotatably supporting the rotary shaft is mounted on one side of the inner peripheral surface of the center bore A double-head swash plate type compressor is provided.

Here, the rotation shaft is supported by the radial bearing, and a cylinder protrusion protruded forward and backward along a center bore edge of the cylinder block.

At this time, the cylinder projection and the radial bearing are disposed on both sides of the refrigerant introduction path of the cylinder block along the longitudinal direction of the rotary shaft.

The radial bearing is formed by joining dissimilar metals each having a different thermal expansion coefficient.

At this time, the radial bearing includes an inner member facing the rotation axis, 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 the cylinder block.

At this time, the inner member may be made of an aluminum alloy, and the outer member may be made of a steel alloy.

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

In addition, a radial bearing seating groove is formed along the circumferential direction on one side of the inner peripheral surface of the center bore, away from the refrigerant introduction path.

At this time, an oil film is formed on one side of the outer circumferential surface of the rotary shaft by the oil flowing into the radial bearing seat.

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

At this time, an oil pocket is formed on one side of the radial bearing, and an oil film is formed on one side of the outer circumferential surface of the rotary shaft by the oil filled in the oil pocket.

At this time, the inner diameter of the radial bearing is preferably equal to the inner diameter of the center bore.

According to another aspect of the present invention, there is provided a cylinder bore comprising: a center bore formed at a center thereof; a plurality of cylinder bores spaced apart from each other circumferentially on a radially outer side of the center bore; A cylinder block in which a refrigerant introduction path is formed; A front housing and a rear housing coupled to the front and rear sides of the cylinder block to form a discharge chamber; A rotary shaft mounted on the center bore of the cylinder block through the front housing and having a refrigerant passage formed along the longitudinal direction thereof and having a refrigerant inlet hole and a refrigerant discharge hole communicating with the refrigerant passage; And a compression means for compressing the working fluid in the cylinder bore in accordance with the rotation of the rotary shaft and discharging the working fluid to the discharge chamber, wherein radial bearing seating grooves are formed on one side of the inner peripheral surface of the center bore, Wherein the compressor is formed in a shape of a cylinder.

Here, a radial bearing is mounted on one side of the radial bearing seat.

At this time, the rotation shaft is supported by the radial bearing, and a cylinder protrusion protruded forward and backward along the center bore edge of the cylinder block.

At this time, the cylinder projection and the radial bearing are disposed on both sides of the refrigerant introduction path of the cylinder block along the longitudinal direction of the rotary shaft.

The radial bearing is formed by joining dissimilar metals each having a different thermal expansion coefficient.

At this time, the radial bearing includes an inner member facing the rotation axis, 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 the cylinder block.

At this time, the inner member may be made of an aluminum alloy, and the outer member may be made of a steel alloy.

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

In addition, an oil film is formed on one side of the outer circumferential surface of the rotating shaft by the oil flowing into the radial bearing seating groove.

At this time, an oil pocket is formed on one side of the radial bearing, and an oil film is formed on one side of the outer circumferential surface of the rotary shaft by the oil filled in the oil pocket.

At this time, the inner diameter of the radial bearing is preferably equal to the inner diameter of the center bore.

According to a preferred embodiment of the present invention, a radial bearing mounting groove is formed on one side of an inner circumferential surface of a center bore, and an oil film is formed in a gap between the rotary shaft and the center bore by oil introduced into the radial bearing mounting groove Therefore, there is an effect that the refrigerant leakage to the peripheral portion of the rotating shaft as in the conventional case is prevented or minimized.

In addition, since the radial bearing for rotatably supporting the rotary shaft is mounted on one side of the inner peripheral surface of the center bore, it is possible to minimize the occurrence of wear due to the load concentrated on the contact portion between the rotary shaft and the center bore.

Further, since the inner member of the radial bearing is formed of a material favorable to rotational sliding of the rotary shaft, the occurrence of abrasion due to friction is minimized.

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

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

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, preferred embodiments of a double-head swash plate type compressor according to the present invention will be described with reference to the accompanying drawings. In this process, the thicknesses of the lines and the sizes of the components shown in the drawings may be exaggerated for clarity and convenience of explanation.

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

It is to be understood that both the foregoing general description and the following detailed description of the present invention are exemplary and explanatory and are not to be construed as limiting the scope or spirit of the invention as disclosed in the accompanying claims. Embodiments that include components replaceable as equivalents in the elements may be included within the scope of the present invention.

Example

FIG. 2 is a sectional view of a double-head swash plate type compressor according to an embodiment of the present invention, and FIG. 3 is a sectional view taken along line A-A of FIG. The bold dotted line arrows shown in Fig. 2 indicate the flow direction of the refrigerant.

2, a double-head swash plate type compressor (hereinafter referred to as a 'compressor') 100 according to an embodiment of the present invention includes a cylinder bore 240 having a center bore 230 and a plurality of cylinder bores 240 formed therein, A front housing 300 and a rear housing 400 coupled to the front and rear sides of the cylinder block 200, a 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) in accordance with rotation of the rotary shaft (500).

The cylinder block 200 includes a front cylinder block 210 and a rear cylinder block 220 which are arranged forward and rearward by engagement. A center bore 230 is formed at an inner center of the front cylinder block 210 and the rear cylinder block 220 so that a rotational shaft 500 to be described later is mounted. A center bore 230 is formed at a radially outer side of the center bore 230 A plurality of cylinder bores 240 are formed.

2 and 3, the center bore 230 and the cylinder bore 240 are communicated with each other by the refrigerant introduction path 250, and the refrigerant flow path 510 of the rotary shaft 500, which will be described later, And the introduced refrigerant flows into the respective cylinder bores 240 through the refrigerant introduction path 250.

Referring back to FIG. 2, the front housing 300 is coupled to the front of the front cylinder block 210. A discharge chamber 310 is formed at one side of the rear surface of the front housing 300 and a valve plate 700 is interposed between the front housing 300 and the front cylinder block 210. The valve plate 700 is formed with a discharge hole 710 through which the cylinder bore 240 of the front cylinder block 210 communicates with the discharge chamber 310 of the front housing 300, A discharge valve 720 for opening and closing the discharge hole 710 is provided on one side of the discharge chamber 310 side.

The rear housing 400 is coupled to the rear of the rear cylinder block 220. A discharge chamber 410 is formed at one side of the front of the rear housing 400 and a valve plate 700 is interposed between the rear housing 400 and the rear cylinder block 220. The valve plate 700 is formed with a discharge hole 710 through which the cylinder bore 240 of the rear cylinder block 220 communicates with the discharge chamber 410 of the rear housing 400, A 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 coupled by fasteners such as bolts to form an overall appearance of the compressor 100.

A rotary 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 on the center bore 230 of the front cylinder block 210 and the rear cylinder block 220 through the shaft hole 320 formed at the center of the front housing 300.

At this time, the cylinder protrusion 211 is protruded forward along the rim of the center bore 230 of the front cylinder block 210 and the cylinder protrusion 221 Is protruded. The cylinder projections 211 and 221 serve to support the rotary shaft 500 together with a radial bearing 800 described later.

A refrigerant passage 510 is formed in the longitudinal direction of the rotary shaft 500 and a refrigerant inlet hole 520 and a refrigerant discharge hole 530 are formed in the outer circumferential surface of the rotary shaft 500 to communicate with the refrigerant passage 510. At this time, the coolant inflow hole 520 is formed at one side of the longitudinal center part of the rotary shaft 500. It is preferable that the refrigerant discharge holes 530 are spaced apart from each other in front of and behind the refrigerant inlet holes 520 so as to correspond to the refrigerant introduction paths 250 described above. The coolant inlet hole 520 and the coolant outlet hole 530 form a predetermined angle with respect to the center axis of the rotary shaft 500.

The refrigerant is sucked into the cylinder block 200 through a suction port (not shown) provided on one side of the outer circumferential surface of the cylinder block 200 and flows through the refrigerant passage 510 inside the rotary shaft 500 through the refrigerant inlet hole 520, Lt; / RTI >

The refrigerant introduced into the refrigerant passage 510 of the rotary shaft 500 flows through the refrigerant introduction passage 250 through the refrigerant introduction hole 250 as the refrigerant discharge hole 530 communicates with the refrigerant introduction passage 250 upon rotation of the rotary shaft 500, (240). The refrigerant introduced into the cylinder bore 240 is compressed by the compression means 600 and the refrigerant compressed by the high pressure is discharged to the discharge chambers 310 and 410 through the discharge holes 710. Then, the high-pressure refrigerant in 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.

The compression means 600 according to an embodiment of the present invention includes a swash plate 610 installed on the rotary shaft 500 at a predetermined inclination angle and a swash plate 610 disposed inside the cylinder bores 240 And a plurality of pistons 620 reciprocating in a straight line.

The swash plate 610 is a means for converting the rotational driving force of the rotating shaft 500 into a linear reciprocating motion of the piston 620. The swash plate 610 is inclined to one side of the hub 630, And the swash plate 610 rotates integrally with the hub 630 when the rotary shaft 500 is rotated. A coolant inlet port 631 is formed at one side of the outer circumferential surface of the hub 630 and communicates with the coolant inlet hole 520 of the rotary shaft 500. A plurality of shoes 611 are provided along the circumferential direction at the rim of the swash plate 610 and the plurality of pistons 620 are slidably supported by the shoes 611 so as to be relatively movable.

At this time, since the swash plate 610 rotates in an inclined state and causes the pistons 620 to move back and forth, the swash plate 610 flows to the left and right due to the axial load to move the swash plate 610, the hub 630, 500 may be deformed.

In order 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 includes a first support protrusion 632 formed to protrude along the rim of both ends of the hub 630 and acting as a damping member and a hub 630 along the inner rim of the center bore 230 of the front and rear cylinder blocks 210, The second support protrusions 212 and 222 protruding from the first support protrusions 212 and 222, respectively.

At one side of the inner circumferential surface of the center bore 230, a radial bearing seating groove 231 is formed along the circumferential direction. A radial bearing 800 is press-fitted into the radial bearing seating groove 231. The inner diameter of the radial bearing 800 and the diameter of the center bore 240 are set so that the inner circumferential surface of the radial bearing 800 mounted on the radial bearing seating groove 231 does not protrude to the inside of the center bore 230 when the radial bearing 800 is mounted, It is preferable that the inner diameters of the two portions are the same.

The radial bearing 800 is mounted on the center bore 230 of the front cylinder block 210 and the center bore 230 of the rear cylinder block 220 to support the rotary shaft 500 in a rotatable manner.

At this time, the radial bearing 800 has a ring-shaped outer member 820 coupled to the outer side of the ring-shaped inner member 810, and 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 thermal expansion coefficients. As an example, the inner member 810 may be made of an aluminum (Al) alloy, and the outer member 820 may be made of a steel alloy such as Fe-C.

More preferably, the inner member 810 may be made of an aluminum alloy (Al-Sn) containing 5.0 to 7.5% of tin (Sn) so as to be advantageous for rotational sliding of the rotating shaft 500. At this time, the cylinder block 200 may be made of an Al-Si alloy material.

On the other hand, an oil pocket 232 is formed on one side of the radial bearing 800. 2, when the radial bearing 800 is press-fitted into the radial bearing seating groove 231, a slight gap (not shown) is formed between the bottom surface of the radial bearing seating groove 231 and the radial bearing 800 a gap formed by the gap forms the oil pocket 232. [

The oil that flows along the outer peripheral surface of the rotary shaft 500 is filled in the oil pocket 232 and the oil collected in the oil pocket 232 flows through the cylinder block 200 and the rotary shaft 500, The oil film 233 (see Fig. 5) is formed.

That is, a clearance space between the bottom surface of the radial bearing seating groove 231 and one surface of the radial bearing 800 forms the oil pocket 232 in the radial bearing seating groove 231, An oil film 233 is formed between the rotary shaft 500 and the cylinder block 200 by the oil to prevent or minimize the leakage of the refrigerant generated along the outer peripheral surface of the rotary shaft 500 .

Conventionally, as the outer circumferential surface of the rotary shaft 500 excessively contacts the inner circumferential surface of the center bore 230, the rotary shaft 500 or the cylinder block 200 is abraded when the rotary shaft 500 rotates. However, according to one embodiment of the present invention, since the cylinder projections 211 and 221 and the radial bearing 800 support the rotary shaft 500, the occurrence of wear can be minimized.

4 is a schematic view showing a supporting structure of a rotating shaft according to an embodiment of the present invention.

The rotary shaft 500 is supported by the cylinder projections 211 and 221 and the radial bearing 800 and the cylinder projections 211 and 221 and the radial bearing 800 are supported by the front and rear cylinder blocks 210 and 220 along the longitudinal direction of the rotary shaft 500 And is disposed at both ends of the refrigerant introduction path 250, respectively.

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

During the compression stroke, one side of the outer circumferential surface of the rotary shaft 500 closely contacts the refrigerant introducing passage 250 to seal the outer circumferential surface of the rotary shaft 500. The support structure provides a sufficient supporting force, while the outer circumferential surface of the rotary shaft 500 and the front and rear cylinder blocks 210, 220 to minimize the wear of the inner circumferential surface of the center bore 230, thereby minimizing the leakage of refrigerant around the rotating shaft 500.

For example, in the case of 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 path 250 is blocked by the rotation of the rotary shaft 500. The outer circumferential surface of the rotary shaft 500 closely contacts the refrigerant introduction path 250, To prevent or minimize the leakage of the refrigerant.

At this time, according to an embodiment of the present invention, the cylinder projections 211 and 221 supporting the rotary shaft 500 and the radial bearing 800 are heavily loaded. Accordingly, a load concentrated excessively on a part of the outer circumferential surface of the rotary shaft 500 corresponding to the conventional refrigerant introduction path 250 is dispersed by the cylinder projections 211 and 221 and the radial bearing 800, thereby minimizing the wear phenomenon.

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

The clearance between the outer circumferential surface of the rotating shaft 500 and the inner circumferential surface of the radial bearing 800 is determined by the outer circumferential surface of the rotating shaft 500 and the circumferential surface of the center bore 230 at the same interval t1 as the gap between the inner circumferential surfaces.

Radial bearing seating grooves 231 are formed on one side of the inner circumferential surface of the center bore 230 along the circumferential direction. A radial bearing 800 is mounted on one side of the radial bearing seating grooves 231.

An oil pocket 232 is formed on one side of the radial bearing 800 when the radial bearing 800 is mounted on the radial bearing seating groove 231. When the rotary shaft 500 is rotated, The oil flowing along the outer circumferential surface of the oil chamber 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. The oil film 233 prevents the refrigerant from leaking along the outer circumferential surface of the rotating shaft 500 Or minimizing it.

6 is a schematic view showing a state in which the inner member of the radial bearing is thermally expanded upon rotation of the rotary shaft according to an embodiment of the present invention, in which the radial bearing is mounted on the center bore of the rear cylinder block.

As described above, the radial bearing 800 is formed by the engagement of the inner member 810 and the outer member 820 having different thermal expansion coefficients, and the thermal expansion coefficient of the inner member 810 is larger than that of the outer member 820 Is larger than the thermal expansion coefficient.

6, the inner peripheral surface of the inner member 810 expands in the direction of the rotating shaft 500. At this time, the outer peripheral surface of the rotating shaft 500 and the inner peripheral surface of the radial bearing 800 The interval t2 between the inner circumferential surfaces is smaller than the interval t1 between the outer circumferential surface of the rotary shaft 500 and the inner circumferential surface of the center bore 230. [ That is, the inner member 810 of the radial bearing 800 is expanded inside the center bore 230 when the temperature of the rotary shaft 500 is increased by the rotation operation of the rotary shaft 500, thereby more firmly supporting the rotary shaft 500.

As described above, since the rotary shaft 500 is supported by the cylinder projections 211 and 221 and the radial bearing 800 according to an embodiment of the present invention, excessive contact between the inner peripheral surface of the rotary shaft 500 and the inner peripheral surface of the center bore 230 It is possible to minimize the occurrence of abrasion due to wear.

An oil film 232 is formed on one side of the radial bearing 800 which is press-fitted into the radial bearing seating groove 231 to form an oil film 233 around the rotation shaft 500, It is possible to prevent or minimize the refrigerant leakage in the vicinity.

Since the radial bearing 800 is formed by the inner member 810 and the outer member 820 having different thermal expansion coefficients, the rotation shaft 500 can be more firmly supported when the heat is generated by the rotation of the rotation shaft 500 .

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 path 300: front housing
400: rear housing 500:
510: Refrigerant channel 520: Refrigerant inlet hole
530: Refrigerant discharge hole 600: Compressing means
610: swash plate 620: piston
630: hub 631: refrigerant inlet
700: Valve plate 800: Radial bearing
810: Inner member 820: Outer member

Claims (23)

A center bore 230 is formed at the center of the center bore 230 and a plurality of cylinder bores 240 are formed at a radially outer side of the center bore 230 in the circumferential direction, A cylinder block 200 in which a refrigerant introduction path 250 communicating with the refrigerant introduction path 250 is formed;
A front housing 300 and a rear housing 400 coupled to the front and rear of the cylinder block 200 to form discharge chambers 310 and 410, respectively;
A refrigerant passage 510 is formed in a longitudinal direction of the cylinder block 200 through the front housing 300 and is connected to the center bore 230 of the cylinder block 200. The refrigerant passage 510 communicates with the refrigerant passage 510, A rotation shaft 500 in which a coolant inlet hole 520 and a coolant outlet hole 530 are formed; And
And compression means (600) for compressing the working fluid from the cylinder bore (240) in accordance with rotation of the rotary shaft (500) and discharging the working fluid to the discharge chambers (310, 410)
Wherein a radial bearing (800) for rotatably supporting the rotary shaft (500) is mounted on one side of the inner peripheral surface of the center bore (230).
[4] The apparatus of claim 1, wherein the rotation shaft (500)
Cylinder projections (211, 221) protruding forward and backward along the rim of the center bore (230) of the cylinder block (200), and the radial bearing (800).
The method of claim 2,
Wherein the cylinder protrusions 211 and 221 and the radial bearing 800 are disposed on both sides of the refrigerant introduction path 250 of the cylinder block 200 along the longitudinal direction of the rotary shaft 500. [ compressor.
The bearing of claim 1, wherein the radial bearing (800)
Wherein the first and second heat exchangers are formed by joining dissimilar metals each having a different thermal expansion coefficient.
[5] The apparatus of claim 4, wherein the radial bearing (800)
An inner member 810 facing the rotary shaft 500 and an outer member 820 facing the cylinder block 200,
Wherein at least one of the inner member (810) and the outer member (820) is made of a material different from that of the cylinder block (200).
The method of claim 5,
Wherein the inner member (810) is made of an aluminum alloy material, and the outer member (820) is made of a steel alloy material.
The method of claim 6,
Wherein the inner member (810) contains 5.0% to 7.5% tin (Sn).
The method according to claim 1,
Wherein a radial bearing mounting groove (231) is formed along a circumferential direction at one side of the inner peripheral surface of the center bore (230), spaced apart from the refrigerant introduction path (250).
The method of claim 8,
And an oil film (233) is formed on one side of the outer circumferential surface of the rotary shaft (500) by the oil flowing into the radial bearing seating groove (231).
The method of claim 8,
And the radial bearing (800) is mounted on one side of the radial bearing seating groove (231).
The method of claim 10,
An oil pocket 232 is formed on one side of the radial bearing 800 and an oil film 233 is formed on one side of the outer circumferential surface of the rotary shaft 500 by the oil filled in the oil pocket 232 Double head swash type compressor.
According to claim 10,
Wherein an inner diameter of the radial bearing (800) is equal to an inner diameter of the center bore (230).
A center bore 230 is formed at the center of the center bore 230 and a plurality of cylinder bores 240 are formed at a radially outer side of the center bore 230 in the circumferential direction, A cylinder block 200 in which a refrigerant introduction path 250 communicating with the refrigerant introduction path 250 is formed;
A front housing 300 and a rear housing 400 coupled to the front and rear of the cylinder block 200 to form discharge chambers 310 and 410, respectively;
A refrigerant passage 510 is formed in a longitudinal direction of the cylinder block 200 through the front housing 300 and is connected to the center bore 230 of the cylinder block 200. The refrigerant passage 510 communicates with the refrigerant passage 510, A rotation shaft 500 in which a coolant inlet hole 520 and a coolant outlet hole 530 are formed; And
And compression means (600) for compressing the working fluid from the cylinder bore (240) in accordance with rotation of the rotary shaft (500) and discharging the working fluid to the discharge chambers (310, 410)
Wherein a radial bearing mounting groove (231) is formed along a circumferential direction at one side of the inner peripheral surface of the center bore (230), spaced apart from the refrigerant introduction path (250).
14. The method of claim 13,
And a radial bearing (800) is mounted on one side of the radial bearing seating groove (231).
[Claim 16] The apparatus of claim 14, wherein the rotation shaft (500)
Cylinder projections (211, 221) protruding forward and backward along the rim of the center bore (230) of the cylinder block (200), and the radial bearing (800).
16. The method of claim 15,
Wherein the cylinder protrusions 211 and 221 and the radial bearing 800 are disposed on both sides of the refrigerant introduction path 250 of the cylinder block 200 along the longitudinal direction of the rotary shaft 500. [ compressor.
15. The apparatus of claim 14, wherein the radial bearing (800)
Wherein the first and second heat exchangers are formed by joining dissimilar metals each having a different thermal expansion coefficient.
[18] The apparatus of claim 17, wherein the radial bearing (800)
An inner member 810 facing the rotary shaft 500 and an outer member 820 facing the cylinder block 200,
Wherein at least one of the inner member (810) and the outer member (820) is made of a material different from that of the cylinder block (200).
19. The method of claim 18,
Wherein the inner member (810) is made of an aluminum alloy material, and the outer member (820) is made of a steel alloy material.
The method of claim 19,
Wherein the inner member (810) contains 5.0% to 7.5% tin (Sn).
14. The method of claim 13,
And an oil film (233) is formed on one side of the outer circumferential surface of the rotary shaft (500) by the oil flowing into the radial bearing seating groove (231).
15. The method of claim 14,
An oil pocket 232 is formed on one side of the radial bearing 800 and an oil film 233 is formed on one side of the outer circumferential surface of the rotary shaft 500 by the oil filled in the oil pocket 232 Double head swash type compressor.
15. The method of claim 14,
Wherein an inner diameter of the radial bearing (800) is equal to an inner diameter of the center bore (230).







KR1020140043541A 2014-04-11 2014-04-11 Double-headed swash plate type compressor KR102027178B1 (en)

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003314441A (en) * 2002-04-18 2003-11-06 Yunikura J:Kk Swash plate compressor
KR100554553B1 (en) 2001-11-21 2006-03-03 가부시키가이샤 도요다 지도숏키 Refrigeration suction mechanism for a piston type compressor and a piston type compressor
KR20060050651A (en) * 2004-08-26 2006-05-19 울박 키코 인코포레이션 The diaphragm-shaped vacuum pump
KR101069088B1 (en) * 2007-06-07 2011-09-30 한라공조주식회사 Compressor

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100554553B1 (en) 2001-11-21 2006-03-03 가부시키가이샤 도요다 지도숏키 Refrigeration suction mechanism for a piston type compressor and a piston type compressor
JP2003314441A (en) * 2002-04-18 2003-11-06 Yunikura J:Kk Swash plate compressor
KR20060050651A (en) * 2004-08-26 2006-05-19 울박 키코 인코포레이션 The diaphragm-shaped vacuum pump
KR101069088B1 (en) * 2007-06-07 2011-09-30 한라공조주식회사 Compressor

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