KR20170100787A - Swash plate type compressor - Google Patents

Swash plate type compressor Download PDF

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Publication number
KR20170100787A
KR20170100787A KR1020160023076A KR20160023076A KR20170100787A KR 20170100787 A KR20170100787 A KR 20170100787A KR 1020160023076 A KR1020160023076 A KR 1020160023076A KR 20160023076 A KR20160023076 A KR 20160023076A KR 20170100787 A KR20170100787 A KR 20170100787A
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KR
South Korea
Prior art keywords
piston
dead center
compression space
swash plate
top dead
Prior art date
Application number
KR1020160023076A
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Korean (ko)
Inventor
이정재
Original Assignee
한온시스템 주식회사
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Priority to KR1020160023076A priority Critical patent/KR20170100787A/en
Publication of KR20170100787A publication Critical patent/KR20170100787A/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
    • F04B27/0804—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 rotary cylinder block
    • F04B27/0808—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 rotary cylinder block having two or more sets of cylinders or pistons
    • 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
    • F04B25/00—Multi-stage pumps
    • F04B25/04—Multi-stage pumps having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • 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
    • F04B27/0804—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 rotary cylinder block
    • F04B27/0821—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 rotary cylinder block component parts, details, e.g. valves, sealings, lubrication
    • F04B27/0839—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 rotary cylinder block component parts, details, e.g. valves, sealings, lubrication valve means, e.g. valve plate
    • 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
    • F04B27/0804—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 rotary cylinder block
    • F04B27/0821—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 rotary cylinder block component parts, details, e.g. valves, sealings, lubrication
    • F04B27/086—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 rotary cylinder block component parts, details, e.g. valves, sealings, lubrication swash plate
    • 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
    • F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
    • F04B27/0878—Pistons
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027—Pulsation and noise damping means

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

Abstract

The present invention relates to a swash plate compressor, and more particularly, to a swash plate type compressor which includes a cylinder block, a rotating shaft rotatably supported by the cylinder block, a swash plate fixed to the rotating shaft by being inclined and rotated together with the rotating shaft, A piston reciprocating within the bore by rotation of the swash plate, and a valve for covering the opening of the bore to form a compression space together with the bore and the piston and for discharging the compressed refrigerant in the compression space , The volume of the compression space can be formed in a predetermined range when the piston is located at the top dead center. Thereby, the noise vibration due to the pulsation generated when the refrigerant compressed in the compression space is discharged through the valve can be reduced.

Description

[0001] SWASH PLATE TYPE COMPRESSOR [0002]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a swash plate type compressor, and more particularly, to a swash plate type compressor capable of compressing a refrigerant by a piston reciprocating by a swash plate.

2. Description of the Related Art [0002] In general, a compressor for compressing a refrigerant in a vehicle cooling system has been developed in various forms. A compressor for compressing refrigerant is reciprocating in which the compressor performs a reciprocating motion, There is a rotary type.

In the reciprocating type, there are a crank type in which the driving force of the driving source is transmitted by a crank to a plurality of pistons, a swash plate type in which a swash plate is installed, a wobble plate type in which a wobble plate is used, Vane rotary using vanes, scroll type using revolving scroll and fixed scroll.

Here, the swash plate compressor reciprocates the piston with a swash plate rotated together with the rotary shaft to compress the refrigerant.

FIG. 1 is a cross-sectional view illustrating a conventional swash plate type compressor, and FIG. 2 is an enlarged cross-sectional view illustrating a compression space when the piston is positioned at a top dead center in the swash plate type compressor of FIG.

1 and 2, a conventional swash plate type compressor includes a rotary shaft 3 rotatably installed, a swash plate 22 slantedly coupled to the rotary shaft 3 and rotated together with the rotary shaft 3, A piston 24 coupled to the swash plate 22 and reciprocating by the rotation of the swash plate 22; bores 122b and 142b reciprocally received by the piston 24; And valves (42, 44) which cover the openings of the bores (142b, 142b) and form compression spaces (C1, C2) together with the bores (122b, 142b) and the piston (24) to discharge the compressed refrigerant.

On the other hand, refrigerant supply holes 122c and 142c for guiding the refrigerant to be compressed into the compression spaces C1 and C2 are formed on the inner circumferential surfaces of the bores 122b and 142b.

In the conventional swash plate type compressor according to this configuration, the swash plate 22 is rotated as the rotation shaft 3 is rotated, and the piston 24 is rotated by the rotation of the swash plate 22, ) And compresses the refrigerant.

More specifically, when the piston 24 is moved from the top dead center to the bottom dead point, the refrigerant to be compressed through the refrigerant supply holes 122c and 142c flows into the compression spaces C1 and C2, Is moved from the bottom dead center to the top dead center, the refrigerant flowing into the compression spaces (C1, C2) is compressed and discharged through the valves (42, 44).

In the conventional swash plate type compressor, when the volume of the compression spaces (C1, C2) is zero when the piston (24) is located at the top dead center so as to increase the compression ratio and increase the discharge pressure of the refrigerant . That is, when the piston 24 is positioned at the top dead center, the piston 24 is formed to be in close contact with the valve 42, 44.

However, in such a conventional swash plate type compressor, noise vibration is deteriorated due to pulsation generated when the refrigerant compressed in the compression spaces (C1, C2) is discharged through the valves (42, 44).

Korean Patent Publication No. 10-2012-0027792

Accordingly, it is an object of the present invention to provide a swash plate type compressor capable of reducing noise vibrations due to pulsation generated when compressed refrigerant is discharged in a compression space.

In order to achieve the above object, the present invention provides a cylinder block comprising: a cylinder block; A rotating shaft rotatably supported on the cylinder block; A swash plate which is inclined to the rotary shaft and rotated together with the rotary shaft; A piston received in the bore of the cylinder block and coupled to the swash plate and reciprocating within the bore by rotation of the swash plate; And a valve for covering the opening of the bore to form a compression space together with the bore and the piston and for discharging the compressed refrigerant in the compression space, wherein when the piston is located at the top dead center, A swash plate type compressor is provided in which the volume is formed in a predetermined range.

When the piston is located at the top dead center, the volume of the compression space may be formed larger than zero (0).

The volume of the refrigerant flowing into the compression space may be smaller than the volume of the compression space when the piston is positioned at the bottom dead center.

The piston may be spaced apart from the valve when the piston is located at the top dead center.

The distance between the valve and the swash plate may be a predetermined value, and the distance between the front end surface of the piston and the swash plate may be shorter than the distance between the valve and the swash plate.

The volume of the compression space may be formed such that the pressure of the compression space is once greater than or equal to a predetermined value until the piston reaches the top dead center from the bottom dead center.

Wherein the valve is configured to open when the pressure in the compression space is greater than or equal to a predetermined value and to close when the pressure in the compression space is less than a predetermined value and wherein the volume of the compression space is such that the piston is at a top dead center The valve can be formed to be opened once.

The volume of the compression space when the rotation axis is located at 0 degrees is set to be 0 degrees when the angle of the rotation axis is 0 degrees when the piston is positioned at the bottom dead center and when the rotation axis is 180 degrees when the piston is positioned at the top dead center, And may be formed so as to be included in the range of 7.5 to 12 times the volume of the compression space when the rotation axis is located in the range of 130 to 180 degrees.

Wherein a refrigerant supply hole is formed in an inner circumferential surface of the bore, the refrigerant supply hole is shielded from the compression space by the piston when the piston is located at the top dead center, The compression space may be formed to be in communication with the compression space.

The refrigerant supply hole may be formed on the opposite side of the valve with respect to the front end surface of the piston when the piston is positioned at the top dead center.

The coolant supply hole may be formed to communicate with the compression space when the piston starts to move from the top dead center to the bottom dead center.

The refrigerant supply hole may be formed at a position at the compression space side end of the refrigerant supply hole at the same position as the front end surface of the piston at the top dead center in the reciprocating motion direction of the piston.

The swash plate type compressor according to the present invention reduces the noise vibration due to the pulsation generated when the compressed refrigerant is discharged in the compression space since the volume of the compression space is formed within a predetermined range when the piston is positioned at the top dead center .

1 is a cross-sectional view of a conventional swash plate type compressor,
FIG. 2 is a cross-sectional view of the swash plate type compressor of FIG. 1, showing an enlarged compression space when the piston is located at the top dead center,
3 is a cross-sectional view illustrating a swash plate type compressor according to an embodiment of the present invention,
Fig. 4 is an enlarged sectional view of the compression space when the piston is located at the top dead center in the swash plate compressor of Fig. 3; Fig.

Hereinafter, a swash plate type compressor according to the present invention will be described in detail with reference to the accompanying drawings.

FIG. 3 is a cross-sectional view illustrating a swash plate compressor according to an embodiment of the present invention, and FIG. 4 is an enlarged cross-sectional view illustrating a compression space when the piston is positioned at the top dead center in the swash plate compressor of FIG.

3 and 4, a swash plate compressor according to an embodiment of the present invention includes a casing 1 having an internal space S, a casing 1 provided inside the casing 1, The compression mechanism 2 and one side thereof are coupled to a driving source (for example, a vehicle engine) (not shown) provided outside the casing 1 and the other side is coupled to the compression mechanism 2, (3) for transmitting the power of the compression mechanism (2) to the compression mechanism (2).

The casing 1 includes a cylinder block 12, 14 in which the compression mechanism 2 is accommodated, a front housing 16 coupled to a front side of the cylinder blocks 12, 14, And a rear housing 18 which is coupled to the rear side of the rear housing 14.

The cylinder block 12, 14 may include a first cylinder block 12 and a second cylinder block 14 which are coupled to each other.

The first cylinder block 12 includes a first cylindrical portion 122 formed in a cylindrical shape and a first annular portion 122 protruding from the outer peripheral portion of the first cylindrical portion 122 toward the second cylinder block 14 124 < / RTI >

A first axial shaft hole 122a through which the rotary shaft 3 is inserted is formed at the center of the first cylindrical portion 122. A first axial hole 122a is formed in the outer circumferential portion of the first cylindrical portion 122, A first bore 122b to be inserted may be formed.

The first shaft hole 122a may be formed in a cylindrical shape passing through the first cylinder block 12 along the axial direction of the first cylinder block 12. [

The first bore 122b extends in the axial direction of the first cylinder block 12 at a portion radially outwardly spaced apart from the first cylinder block 12 from the first axial bore 122a, And may be formed in a cylindrical shape passing through the cylinder block 12. [

The plurality of first bores 122b are arranged along the circumferential direction of the first cylinder block 12 with respect to the first axial bore 122a, .

The first cylindrical portion 122 may have a first coolant supply hole 122c communicating the first axial hole 122a and the first bore 122b.

The first coolant supply hole 122c may be formed through the first cylindrical portion 122 from the inner circumferential surface of the first shaft hole 122a to the inner circumferential surface of the first bore 122b.

The first coolant supply hole 122c may be formed to communicate the plurality of first bores 122b with the first axial flow hole 122a.

The second cylinder block 14 may be formed to be symmetrical with respect to the first cylinder block 12.

That is, the second cylinder block 14 includes a second cylindrical portion 142 formed in a cylindrical shape and a second annular portion 142 protruding from the outer peripheral portion of the second cylindrical portion 142 toward the first cylinder block 12, (144).

A second shaft hole 142a through which the rotation shaft 3 penetrating the first shaft hole 122a is inserted is formed in the center of the second shaft portion 142, And a second bore 142b into which the other end of the piston 24 inserted in the first bore 122b is inserted may be formed on the outer peripheral side.

The second shaft hole 142a may be formed in a cylindrical shape passing through the second cylinder block 14 along the axial direction of the second cylinder block 14. [

The second bore 142b extends from the second axial passage 142a along the axial direction of the second cylinder block 14 at a radially outwardly spaced apart portion of the second cylinder block 14, And may be formed into a cylindrical shape passing through the cylinder block 14. [

The second bores 142b are formed in a number corresponding to the number of the first bores 122b and a plurality of the second bores 142b are formed in the second bores 142b, 2 cylinder block 14 in the circumferential direction.

The second cylindrical portion 142 may be formed with a second coolant supply hole 142c for communicating the second axial hole 142a with the second bore 142b.

The second coolant supply hole 142c may extend through the second cylindrical portion 142 from the inner circumferential surface of the second shaft hole 142a to the inner circumferential surface of the second bore 142b.

The second coolant supply hole 142c may be formed to communicate the plurality of second bores 142b with the second axial flow hole 142a.

The first cylinder block 12 and the second cylinder block 14 are formed such that the first annular portion 124 and the second annular portion 144 are coupled to each other to form the first cylindrical portion 122 And a space S may be formed between the first cylindrical portion 142 and the second cylindrical portion 142.

In the space S, a swash plate 22 to be described later can be accommodated.

One end of the piston 24 is inserted into the first bore 122b and the other end of the piston 24 is inserted into the second bore 142b. To the swash plate 22 to be described later.

Meanwhile, the space S may communicate with a suction pipe (not shown) for guiding the refrigerant to be compressed into the casing 1, and may be a refrigerant suction space.

The front housing 16 is fastened to the first cylinder block 12 so as to cover the first cylinder part 122 on the opposite side of the second cylinder block 14 with respect to the first cylinder block 12. [ .

The front housing 16 has a through hole 162 through which one end of the rotary shaft 3 is inserted so that one end of the rotary shaft 3 protruding from the first axial shaft hole 122a is coupled to the driving source (not shown) Can be formed.

The front housing 16 may be provided with a first discharge chamber 164 for receiving the refrigerant discharged from the first bore 122b.

The first discharge chamber 164 may communicate with a discharge pipe (not shown) for guiding the compressed refrigerant to the outside of the casing 1.

A first valve 42 for selectively communicating the first bore 122b and the first discharge chamber 164 may be interposed between the first cylinder block 12 and the front housing 16 have.

The first valve 42 covers the opening of the first bore 122b on the side of the first discharge chamber 164 and cooperates with the first bore 122b and the piston 24 to be described later in the first compression space C1 ) Can be formed.

When the pressure in the first compression space C1 is equal to or greater than a predetermined value, the first valve 42 is formed in a plate spring manner, for example, The compressed refrigerant communicated with the chamber 164 is discharged from the first compression space C1 to the first discharge chamber 164 and closed when the pressure in the first compression space C1 is less than a predetermined value May be formed to shield the first compression space (C1) and the first discharge chamber (164) to block the flow of the refrigerant between the first compression space (C1) and the first discharge chamber (164).

The rear housing 18 is fastened to the second cylinder block 14 so as to cover the second cylindrical portion 142 on the opposite side of the first cylinder block 12 with respect to the second cylinder block 14. [ .

A second discharge chamber 184 may be formed in the rear housing 18 to receive the refrigerant discharged from the second bore 142b.

The second discharge chamber 184 may communicate with a discharge pipe (not shown) for guiding the compressed refrigerant to the outside of the casing 1.

A second valve 44 for selectively communicating the second bore 142b and the second discharge chamber 184 may be interposed between the second cylinder block 14 and the rear housing 18 have.

The second valve 44 covers the opening of the second bore 142b on the side of the second discharge chamber 184 and cooperates with the second bore 142b and the piston 24 to be described later in the second compression space C2 ) Can be formed.

When the pressure in the second compression space C2 is equal to or greater than a predetermined value, the second valve 44 is formed in a plate spring manner, for example, The refrigerant compressed by the seal 184 is discharged from the second compression space C2 to the second discharge chamber 184 and is closed when the pressure in the second compression space C2 is less than a predetermined value May be formed to shield the second compression space (C2) and the second discharge chamber (184) to block the refrigerant flow between the second compression space (C2) and the second discharge chamber (184).

The compression mechanism 2 includes a swash plate 22 which is inclined to the rotary shaft 3 and rotates together with the rotary shaft 3 and a swash plate 22 housed in the first bore 122b and the second bore 142b, And a piston 24 coupled to the first bore 22 and reciprocating within the first bore 122b and the second bore 142b by rotation of the swash plate 22. [

The swash plate 22 is formed in a disc shape and can be slantingly fastened to the rotary shaft 3 in the space S of the cylinder block 12,

The space S of the cylinder block 12 and the refrigerant passage 32 of the rotary shaft 3 are communicated with the swash plate 22 so that the space S of the cylinder block 12, A coolant passage hole 222 for guiding the coolant introduced into the coolant passage 32 to be described later of the rotary shaft 3 can be formed.

The piston 24 is formed in a cylindrical shape and passes through the space S of the cylinder block 12 and 14 so that one end is inserted into the first bore 122b and the other end is inserted into the second bore 142b ). That is, the piston 24 is provided in plural, and each piston 24 can be inserted into one of the plurality of the first bores 122b and one of the plurality of the second bores 142b.

 The length of the piston 24 in the axial direction is such that one end of the piston 24 is not separated from the first bore 122b when the piston 24 is moved toward the second bore 142b, The other end of the piston 24 may not be separated from the second bore 142b when the piston 24 is moved toward the first bore 122b. The outer diameter of the piston 24 may be equal to the inner diameter of the first bore 122b and the inner diameter of the second bore 142b.

The piston 24 may be coupled to an outer circumferential portion of the swash plate 22 at a middle portion accommodated in the space S of the cylinder block 12, That is, the swash plate 22 and the swash plate 22 can be coupled to the piston 24 so as to be rotatable relative to the piston 24.

The rotary shaft 3 may be formed in a cylindrical shape extending in one direction.

One end of the rotation shaft 3 is inserted into the cylinder block 12, 14 (more precisely, the first shaft hole 122a and the second shaft hole 142a) so as to be rotatably supported, and the other end May penetrate through the through hole 162 of the front housing 16 and protrude to the outside of the casing 1 and may be connected to the driving source (not shown).

The refrigerant flowing from the refrigerant passage hole 222 of the swash plate 22 is introduced into the rotary shaft 3 through the first refrigerant supply hole 122c and the second refrigerant supply hole 122c of the cylinder block 12, And a coolant passage 32 for guiding the coolant to the coolant passage 142c.

The refrigerant passage 32 includes a first discharge port 322 selectively communicating with the first refrigerant supply hole 122c and a second discharge port 324 selectively communicating with the second refrigerant supply hole 142c. . ≪ / RTI >

The first discharge port 322 is communicated with the first refrigerant supply hole 122c in the suction stroke among the plurality of first refrigerant supply holes 122c in accordance with the rotation of the rotary shaft 3, 32) to the outer circumferential surface of the rotating shaft (3).

The second discharge port 324 is communicated with the second refrigerant supply hole 142c in the suction stroke of the plurality of second refrigerant supply holes 142c in accordance with the rotation of the rotary shaft 3, 32 to the outer peripheral surface of the rotary shaft 3 through the other side of the rotary shaft 3.

In the swash plate type compressor according to this embodiment, when the power is transmitted from the driving source (not shown) to the rotating shaft 3, the rotating shaft 3 and the swash plate 22 can be rotated together.

Accordingly, the piston 24 converts the rotational motion of the swash plate 22 into a rectilinear motion so that the cylinder block 12, 14 (more precisely, the first bore 122b and the second bore 142b) And can reciprocate in the inside.

Accordingly, the space S of the cylinder block 12, the refrigerant passage hole 222, the refrigerant passage 32, the first refrigerant supply hole 122c, The refrigerant is sucked into the first compression space (C1) and the second compression space (C2) through the second refrigerant supply hole (142c) and compressed so that the first discharge chamber (164) and the second discharge chamber ). ≪ / RTI >

More specifically, when the piston 24 is moved toward the first compression space C1, it is preferable that the piston 24 is moved in the first compression space C1, The compression stroke is performed while the front end surface (hereinafter referred to as the first piston front end surface) 241 on the side of the first compression space C1 side of the piston 24 is moved from the bottom dead center to the top dead center, and in the second compression space C2 The suction stroke can be performed while the front end surface (hereinafter referred to as the second piston front end surface 242) of the piston 24 on the side of the second compression space C2 is moved from the top dead center to the bottom dead center.

That is, in the case of the first compression space C1, the first refrigerant supply hole 122c and the refrigerant passage 32 are shielded from each other, and the volume of the first compression space C1 is from the bottom dead center to the top dead center And the refrigerant flowing into the first compression space C1 before being shielded between the first refrigerant supply hole 122c and the refrigerant passage 32 is reduced by the first piston front end surface 241, The refrigerant can be compressed by the volume reduction of the first compression space (C1). When the pressure of the refrigerant compressed in the first compression space C1 becomes equal to or greater than a predetermined value, the first valve 42 is opened and discharged to the first discharge chamber 164 .

In the case of the second compression space C2, the second refrigerant supply hole 142c and the refrigerant passage 32 communicate with each other, and the volume of the second compression space C2 moves from the top dead center to the bottom dead center The refrigerant is increased by the second piston front end surface 242 of the cylinder block 12 and 14 due to the increase in the volume of the second compression space C2, Through the refrigerant passage hole 222 of the swash plate 22, the refrigerant passage 32 of the rotary shaft 3 and the second refrigerant supply hole 142c of the cylinder block 12, 2 compression space C2. At this time, the second valve (44) may block the second compression space (C2) and the second discharge chamber (184).

On the other hand, when the piston 24 is moved toward the second compression space C2, in the first compression space C1, the first piston end face 241 is moved from the top dead center to the bottom dead center, In the second compression space C2, the compression stroke can be performed while the second piston front end surface 242 is moved from the bottom dead center to the top dead center. The detailed description thereof will be omitted since it is the same as described above.

Meanwhile, the refrigerant discharged to the first discharge chamber 164 and the second discharge chamber 184 may be discharged to the outside of the casing 1 through the discharge pipe (not shown).

In this process, pulsation occurs when the refrigerant compressed in the first compression space (C1) or the second compression space (C2) is discharged through the first valve (42) or the second valve (44) , The noise vibration of the compressor may be deteriorated by such pulsation.

Considering this, in the case of this embodiment, as the volume of the compression spaces (C1, C2) is formed within a predetermined range when the piston (24) is located at the top dead center, the noise vibration due to pulsation can be reduced .

More specifically, the noise vibration due to the pulsation is proportional to the pressure of the refrigerant compressed in the compression spaces (C1, C2). In this embodiment, in order to reduce the pressure of the refrigerant and reduce the noise vibration due to the pulsation, 24 are positioned at the top dead center, the volume of the compression spaces (C1, C2) can be made larger than zero (0).

The volume of the first compression space C1 is set to a predetermined value when the piston 24 is positioned at the top dead center (as close as possible to the first valve 42) May be formed larger than zero (0).

Here, when the piston 24 is positioned at the top dead center, the first piston front end surface 241 is spaced apart from the first valve 42, so that when the piston 24 is positioned at the top dead center, The volume of the first compression space C1 may be formed larger than zero.

Since the axial length of the cylinder block 12 or 14 is increased or the axial length of the piston 24 is shortened, when the piston 24 is positioned at the top dead center, May be spaced apart from the first valve 42. If the axial length of the cylinder blocks 12 and 14 is increased, the size, weight, and cost of the cylinder blocks 12 and 14 may be increased. Therefore, the axial length of the piston 24 may be short May be desirable. That is, as in the present embodiment, the distance D1 from the coupling portion of the swash plate 22 to the piston 24 to the first valve 42 is formed to a predetermined value, and the swash plate 22 Of the swash plate 22 to the first piston front end face 241 from the engagement position of the swash plate 22 with the piston 24 is smaller than the distance D2 between the first valve 42 The distance D1 is shorter than the distance D1. In this case, since the axial lengths of the cylinder blocks 12 and 14 are not increased, the size, weight, and cost of the cylinder blocks 12 and 14 are not increased and the axial length of the piston 24 is reduced The size, weight and cost of the piston 24 can be reduced.

When the volume of the first compression space C1 is formed to be larger than zero when the piston 24 is positioned at the top dead center (as close as possible to the first valve 42) (0), the compression ratio of the first compression space (C1) can be reduced. That is, when the volume of the refrigerant flowing into the first compression space C1 reaches the first compression space C1 when the piston 24 is positioned at the bottom dead center (as far as possible from the first valve 42) As shown in FIG. The volume of the refrigerant flowing into the first compression space C1 is set such that the first piston front end face 241 and the piston 24 are positioned at the bottom dead center when the piston 24 is positioned at the top dead center. The inner circumferential surface of the first bore 122b and the first piston distal end surface 241 may be formed. Accordingly, the pressure of the refrigerant compressed in the first compression space (C1) is reduced, and the noise vibration of the compressor due to the pulsation and the ripple thereof can be reduced.

On the other hand, when the volume of the first compression space (C1) is excessively large when the piston (24) is located at the top dead center, the pressure of the refrigerant may be excessively reduced and the compression efficiency may be lowered. In consideration of this, in the present embodiment, the volume of the first compression space (C1) is set so that when the piston (24) is located at the top dead center, the volume of the first compression space (1) such that the refrigerant pressure in the first compression space (C1) is greater than or equal to the predetermined value once, until the piston (24) reaches the top dead center from the bottom dead center And a volume in which the valve 42 is opened and closed once).

More specifically, the first valve 42 is opened when the refrigerant pressure in the first compression space C1 is equal to or greater than a predetermined value as described above, and the refrigerant pressure in the first compression space C1 is increased in advance When the piston 24 is below the determined value, the piston 24 can be opened and closed several times from the bottom dead center to the top dead center. That is, when the piston 24 is moved from the bottom dead center to the top dead center, the refrigerant pressure in the first compression space C1 becomes equal to or greater than a predetermined value before the piston 24 reaches the top dead center, The first valve 42 is opened and the refrigerant can be discharged first. After the refrigerant has been firstly discharged, the refrigerant pressure in the first compression space C1 becomes less than a predetermined value, so that the first valve 42 can be closed. The piston 24 is continuously moved to the top dead center after the first valve 42 has been opened and closed once and the piston 24 has not reached the top dead center yet, The refrigerant pressure is again greater than a predetermined value, and the first valve 42 is opened and closed again so that the refrigerant can be discharged secondarily. And, on the same principle, the first valve 42 can be opened and closed several times when the piston 24 is moved once from the bottom dead center to the top dead center. Since the noise vibration due to the pulsation is proportional to the number of times of opening and closing of the first valve 42, when the piston 24 moves once from the bottom dead center to the top dead center, The noise vibration due to the pulsation can be increased.

In consideration of this, in this embodiment, when the piston 24 is positioned at the bottom dead center, the angle of the rotary shaft 3 is set to 0 degree, and when the piston 24 is positioned at the top dead center, The volume of the first compression space C1 is set such that when the rotation axis 3 is located in the range of 130 to 180 degrees, May be formed so as to be included in a range of 7.5 times to 12 times as large as the volume of the capacitor C1. The first valve 42 may be formed to open at a pressure of 3 bar to 7 bar higher than the pressure of the first discharge chamber 164 in the first compression space C1. Thereby, when the piston 24 is positioned at the top dead center, the volume of the first compression space C1 is greater than zero, and the piston 24 is moved from its bottom dead center to its top dead center, (The volume in which the first valve 42 is opened and closed only once) such that the refrigerant pressure in the first compression space C1 becomes equal to or greater than the predetermined value once. Accordingly, the refrigerant pressure in the first compression space (C1) is reduced so as to reduce the pulsation, but is not smaller than the predetermined value so that the compression efficiency is prevented from lowering and the number of times of opening and closing of the first valve (42) The pulsation can be further reduced.

Meanwhile, the first refrigerant supply hole 122c may be formed so as to be shielded by the piston 24 at a top dead center of the piston 24 so as to prevent backflow of the refrigerant. More specifically, at the top dead center, the first piston front end surface (241) and the first valve (42) are spaced apart from each other, and at least a part of the first refrigerant supply hole (122c) The first refrigerant supply hole 122c is always formed in the first compression space C1 regardless of the position of the piston 24 when the first valve 42 is formed with the front end surface 241 as a reference, . In this case, the compressed refrigerant may flow back to the refrigerant passage 32 of the rotary shaft 3 through the first refrigerant supply hole 122c. In consideration of this, in the present embodiment, the first refrigerant supply hole 122c is formed on the opposite side of the first valve 42 with respect to the first piston front end surface 241 at the top dead center, When the refrigerant is compressed in the first compression space C1, it can be covered by the outer peripheral surface of the piston 24 and shielded from the first compression space C1. Accordingly, the compressed refrigerant can be prevented from flowing back to the refrigerant passage 32 of the rotary shaft 3 through the first refrigerant supply hole 122c.

The first refrigerant supply hole 122c may be formed to communicate with the first compression space C1 when the piston 24 starts to move from the top dead center to the bottom dead point so that suction loss is prevented . More specifically, in the reciprocating motion direction of the piston 24, the end of the first refrigerant supply hole 122c on the side of the first compression space C1 side is connected to the first piston front end surface 241 at the top dead center The piston 24 is moved toward the bottom dead center in the initial stage of the suction stroke but the first refrigerant supply hole 122c and the first compression space C1 Can not communicate with each other, so that suction loss may occur. In consideration of this, in the reciprocating motion direction of the piston 24, the end of the first refrigerant supply hole 122c on the side of the first compression space C1 is connected to the first piston line The first refrigerant supply hole 122c is communicated with the first compression space C1 when the piston 24 starts to move from the top dead center to the bottom dead point by being disposed to be in the same position as the end face 241 . Accordingly, it is possible to prevent the suction loss from occurring at the beginning of the suction stroke.

Although the noise vibration due to the pulsation of the present embodiment, prevention of lowering of compression efficiency, reduction in size, weight and cost of the piston, prevention of refrigerant backflow, and prevention of suction loss have been described above with the first compression space (C1) side as an example, The second compression space C2 side may also be formed on the same principle as the first compression space C1 side. The detailed description thereof will be omitted since it is the same as described above.

In the case of the present embodiment, a so-called capacity-fixed double-head swash plate type compressor in which the inclination angle between the swash plate 22 and the rotary shaft 3 is fixed and compression spaces C1 and C2 are formed on both sides of the piston 24, Although the description has been made by way of example, the technical idea of reducing noise vibration, preventing compression efficiency, reducing the size, weight and cost of a piston, preventing reverse flow of refrigerant, and preventing suction loss due to pulsation of the present embodiment, A variable displacement swash plate type compressor in which the inclination angle between the swash plate and the rotary shaft is adjusted and a compression space is formed only on one side of the piston).

3: rotation shaft 12, 14: cylinder block
22: swash plate 24: piston
42, 44: valves 122c, 142c: refrigerant supply holes
122b, 142b: bore 241, 242:
C1, C2: Compressed space D1: Distance from swash plate to valve
D2: Distance from swash plate to piston cross section

Claims (12)

Cylinder blocks (12, 14);
A rotating shaft (3) rotatably supported on the cylinder block (12, 14);
A swash plate 22 inclined to the rotary shaft 3 and rotated together with the rotary shaft 3;
Is received in the bores 122b and 142b of the cylinder block 12 and 14 and is coupled to the swash plate 22 and is reciprocated inside the bores 122b and 142b by the rotation of the swash plate 22 A piston 24; And
The compression spaces C1 and C2 are formed together with the bores 122b and 142b and the piston 24 so as to cover the openings of the bores 122b and 142b so that the refrigerant compressed in the compression spaces C1 and C2 (42, 44) for discharging the liquid,
Wherein a volume of the compression space (C1, C2) is formed in a predetermined range when the piston (24) is located at the top dead center. The method according to claim 1,
Wherein the volume of the compression space (C1, C2) is greater than zero when the piston (24) is located at the top dead center. 3. The method of claim 2,
Wherein the volume of the refrigerant flowing into the compression spaces (C1, C2) is smaller than the volume of the compression spaces (C1, C2) when the piston (24) is positioned at the bottom dead center. 3. The method of claim 2,
Characterized in that the piston (24) is spaced from the valve (42, 44) when the piston (24) is located at the top dead center. 5. The method of claim 4,
The distance D1 between the valves 42 and 44 and the swash plate 22 is formed to a predetermined value,
The distance D2 between the front end surfaces 241 and 242 of the piston 24 and the swash plate 22 is shorter than the distance D1 between the valves 42 and 44 and the swash plate 22. [ . The method according to claim 1,
The volume of the compression space (C1, C2) is set such that the pressure of the compression space (C1, C2) is once greater than or equal to a predetermined value until the piston (24) reaches the top dead center from the bottom dead center Expression compressor. The method according to claim 1,
The valve (42,44) is opened when the pressure in the compression space (C1, C2) is above a predetermined value and is formed to close when the pressure in the compression space (C1, C2) is below a predetermined value,
Wherein the volume of the compression spaces (C1, C2) is formed such that the valves (42, 44) are opened once until the piston (24) reaches a top dead center from the bottom dead center. 8. The method according to claim 6 or 7,
When the angle of the rotary shaft 3 is set to 0 degrees when the piston 24 is positioned at the bottom dead center and the angle of the rotary shaft 3 is set to 180 degrees when the piston 24 is positioned at the top dead center,
The volume of the compression space (C1, C2) when the rotation axis (3) is located at 0 degrees is set such that the volume of the compression space (C2, C2) And is formed so as to be included in the range of 7.5 times to 12 times. 5. The method of claim 4,
The inner surfaces of the bores 122b and 142b are provided with coolant supply holes 122c and 142c through which the coolant flows,
The refrigerant supply holes 122c,
Is shielded by the piston (24) with the compression space (C1, C2) when the piston (24) is located at the top dead center,
And is configured to communicate with the compression spaces (C1, C2) when the piston (24) is moved from the top dead center to the bottom dead center. 10. The method of claim 9,
The refrigerant supply holes 122c and 142c are formed on opposite sides of the valves 42 and 44 with respect to the front end surfaces 241 and 242 of the piston 24 when the piston 24 is positioned at the top dead center A swash plate compressor. 10. The method of claim 9,
The refrigerant supply holes 122c and 142c are formed to communicate with the compression spaces C1 and C2 when the piston 24 starts to move from the top dead center to the bottom dead center. 12. The method of claim 11,
The ends of the refrigerant supply holes 122c and 142c in the compression spaces C1 and C2 of the refrigerant supply holes 122c and 142c in the reciprocating direction of the piston 24 are connected to the ends of the pistons 24 And is formed at the same position as the front end faces (241, 242).
KR1020160023076A 2016-02-26 2016-02-26 Swash plate type compressor KR20170100787A (en)

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Application Number Priority Date Filing Date Title
KR1020160023076A KR20170100787A (en) 2016-02-26 2016-02-26 Swash plate type compressor

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