KR101345154B1 - Variable swash plate type compressor - Google Patents

Variable swash plate type compressor Download PDF

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Publication number
KR101345154B1
KR101345154B1 KR1020120126641A KR20120126641A KR101345154B1 KR 101345154 B1 KR101345154 B1 KR 101345154B1 KR 1020120126641 A KR1020120126641 A KR 1020120126641A KR 20120126641 A KR20120126641 A KR 20120126641A KR 101345154 B1 KR101345154 B1 KR 101345154B1
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KR
South Korea
Prior art keywords
swash plate
hub
arm
hinge pin
shaft
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KR1020120126641A
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Korean (ko)
Inventor
차용웅
박만희
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현대자동차주식회사
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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
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • 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
    • 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
    • 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
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/002—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for driven by internal combustion engines
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/36—Pulleys
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/02—Gearings for conveying rotary motion by endless flexible members with belts; with V-belts
    • 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
    • F05B2260/00—Function
    • F05B2260/96—Preventing, counteracting or reducing vibration or noise

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

Abstract

The present invention includes a shaft which rotates around an axis; a rotor with a rotor arm which is mounted on the shaft; a hinge pin of which one end is connected to the rotor arm; a swash plate which is joined to a hub fitted to the shaft, wherein the hub has a hub arm to which the other end portion of the hinge pin is connected and which is rotated to enable the variation of an inclined angle of the swash plate to the shaft according to the rotation position of the hub arm. Both end portions of the hinge pin are joined to the rotor arm and the hub arm to be rotated respectively. The present invention with the configuration described above is provided to improve the responsibility of a compressor as the hinge pin is rotated more actively according to the inclined angle of the swash plate and to reduce vibration more efficiently by reducing the amount of unbalance.

Description

가변 사판형 컴프레서{Variable swash plate type compressor}Variable swash plate type compressor {Variable swash plate type compressor}

본 발명은 사판의 경사각 조절을 통해 토출용량을 가변할 수 있는 가변 사판형 컴프레서에 관한 것으로서 더욱 상세하게는 사판에 작용하는 언밸런스 변화폭을 감소시켜 진동을 효율적으로 감쇠시킬 수 있는 가변 사판형 컴프레서에 관한 것이다.
The present invention relates to a variable swash plate type compressor capable of varying the discharge capacity by adjusting the inclination angle of the swash plate, and more particularly, to a variable swash plate type compressor capable of efficiently attenuating vibrations by reducing the unbalance change width acting on the swash plate. will be.

차량의 공조장치는 차량 내부의 공기를 쾌적한 상태로 유지시켜주는 장치로서, 차량의 내부온도에 따라 냉풍 또는 온풍이 토출되도록 구성된다.The air conditioner of the vehicle is a device for maintaining the air inside the vehicle in a comfortable state, and configured to discharge cold or warm air according to the internal temperature of the vehicle.

이중, 차량 내부로 토출되는 냉풍은 냉매가 압축, 응축, 팽창, 증발 과정을 반복하는 동안 블로워모터에 의해 송풍되는 바람이 냉각되어 생성된다.Among these, the cold air discharged into the vehicle is generated by cooling the wind blown by the blower motor while the refrigerant is repeatedly compressed, condensed, expanded, and evaporated.

상기 냉매는 엔진 크랭크샤프트의 풀리와 연결되어 동력을 전달받도록 구성된 컴프레서에 의해 압축된다. The refrigerant is compressed by a compressor configured to be connected to the pulley of the engine crankshaft to receive power.

상기 컴프레서는 증발기(evaporator)에서 토출된 저온저압의 기체상태인 냉매를 고온고압의 기체상태로 압축하는 역활을 하며 상기 냉매를 응축기(condenser)로 토출하도록 구성된다.The compressor serves to compress the low temperature low pressure gaseous refrigerant discharged from the evaporator into the high temperature high pressure gaseous state and is configured to discharge the refrigerant to the condenser.

상기 컴프레서는 여러 가지 타입이 적용되되, 대표적으로는 사판형 타입(Swash plate type), 베인로타리타입(Vane rotary type), 와블플레이트 타입(Wobble plate type)이 널리 사용되고 있다.Various types of compressors are applied, and typically, a swash plate type, a vane rotary type, and a wobble plate type are widely used.

이중, 사판형 컴프레서는 사판의 경사각이 고정된 용량 고정형과 사판의 경사각이 조절될 수 있는 용량 가변형으로 구분될 수 있으며 종래의 용량 가변형(사판 가변형) 컴프레서의 구조는 도 1 에 도시되었다.Among them, the swash plate type compressor may be classified into a capacity fixed type in which the inclination angle of the swash plate is fixed and a variable capacity type in which the inclination angle of the swash plate is adjustable, and the structure of the conventional variable displacement type (swash plate variable type) compressor is illustrated in FIG. 1.

도 1a 을 참조하면, 상기 컴프레서는 엔진의 크랭크샤프트에 벨트로 연결되어 축 회전하는 샤프트에 로터와 사판이 나란히 장착되도록 구성된다. 상기 로터에는 사판을 향하여 로터암이 돌출되며 상기 로터암에는 장공(長孔)형의 슬롯홀이 형성된다. 상기 사판은 허브에 결합되어 샤프트에서 경사각이 가변될 수 있도록 장착되되, 상기 허브에는 로터를 향하여 허브암이 돌출된다. 상기 허브암 끝단에는 힌지핀의 일단이 고정장착되며, 상기 힌지핀의 타단은 슬롯홀에서 활주가능하도록 구속된다. Referring to Figure 1a, the compressor is configured such that the rotor and the swash plate are mounted side by side on the shaft that is connected to the crankshaft of the engine by the belt shaft rotation. The rotor arm protrudes toward the swash plate, and the rotor arm is formed with a slot hole having a long hole shape. The swash plate is coupled to the hub is mounted so that the inclination angle on the shaft is variable, the hub arm protrudes toward the rotor. One end of the hinge pin is fixedly mounted to the hub arm end, and the other end of the hinge pin is slidably slidable in the slot hole.

상기와 같은 가변 사판형 컴프레서는 사판의 경사각도를 조절함으로서 토출용량(즉, 사판에 연결된 피스톤의 스트로크 크기)을 가변시킬 수 있다.
The variable swash plate type compressor as described above may vary the discharge capacity (that is, the stroke size of the piston connected to the swash plate) by adjusting the inclination angle of the swash plate.

하지만, 상기와 같은 종래의 가변 사판형 컴프레서의 경우 사판의 경사각이 변함에 따라서 무게중심이 달라지고 이에 따라서 진동이 발생하는 문제점이 있었다.However, in the case of the conventional variable swash plate type compressor as described above, there is a problem in that the center of gravity is changed as the inclination angle of the swash plate is changed and thus vibration is generated.

사판의 경사각 변경 시, 샤프트와 로터 및 사판은 무게중심이 변하지 않는 반면, 허브와 힌지핀은 무게중심이 변함으로 상기와 같은 무게중심 변화는 진동을 유발하는 주원인이 되었다(도 4 참조).When the inclination angle of the swash plate is changed, the shaft, the rotor, and the swash plate do not change the center of gravity, whereas the hub and hinge pins change the center of gravity, such that the above-described center of gravity change causes vibration (see FIG. 4).

경사각 변경에 따른 진동을 감쇠시키기 위해서 종래에는 허브에 밸러스웨이트를 형성하여 사판의 편심량(회전체의 중량과 무게중심의 곱)을 줄임으로서 진동 발생크기를 줄였으나, 사판의 무게중심 또한 변하고 허브 자체의 무게 증대로 언밸러스량(회전축을 중심으로 1cmm 거리에 위치하는 상당 중량)이 증대하여 진동감쇄 효과는 제한적이었다. In order to attenuate the vibration caused by the change of the inclination angle, conventionally, the ballast weight was formed on the hub to reduce the size of vibration by reducing the eccentricity of the swash plate (the product of the weight of the rotating body and the center of gravity), but the weight center of the swash plate also changed and the hub itself The increase in the weight of the increased the unbalanced amount (equivalent weight located at a distance of 1 cmm about the rotation axis), and the vibration damping effect was limited.

도 1b 를 참조하여, 사판의 경사각과 작용하는 모멘트의 관계를 더욱 상세히 살펴보면, 도 1b 의 윗쪽 그림에서와 같이 사판을 기울이는 힘(경사각을 증가시키는 힘)은 사판에 수직방향으로 가해지는 양측 피스톤들의 합력(Pd: 송출압력, Ps: 흡입압력)에 대응하는 '펌핑모멘트(pumping moment)'로 형성된다. 그리고, 도 1b 의 아랫쪽 그림에서와 같이 사판을 세우는 힘(사판이 로터와 평행하도록 경사각을 감소시키는 힘)은 엔진 크랭크샤프트를 통해 전달되는 토크에 의해 생성되는 'PC모멘트'로 형성된다. Referring to Fig. 1b, in more detail the relationship between the inclination angle of the swash plate and the moment acting, as shown in the upper figure of Fig. 1b the force to tilt the swash plate (force to increase the inclination angle) of the two pistons applied perpendicular to the swash plate It is formed as a 'pumping moment' corresponding to the force (Pd: discharge pressure, Ps: suction pressure). Then, as shown in the lower figure of Fig. 1b, the force for raising the swash plate (the force for decreasing the inclination angle so that the swash plate is parallel to the rotor) is formed by the 'PC moment' generated by the torque transmitted through the engine crankshaft.

하지만, 사판을 기울일 때는 (Pd 와 Ps의) 합력이 가해지는 방향과 힌지핀의 이동방향에 ('A' 각도 만큼) 차이가 발생하여 초기 응답성을 저하시키며, 사판을 세울 때는 (Pc 의) 합력과 힌지핀의 이동방향에 ('B' 각도 만큼) 차이가 발생하여 응답성이 저하됐다. However, when tilting the swash plate, there is a difference (by 'A' angle) between the direction in which the force (of Pd and Ps) is applied and the moving direction of the hinge pin, which lowers the initial responsiveness. There was a difference in the direction of movement of the force and hinge pin (by the 'B' angle), resulting in poor response.

이러한, 응답성의 저하는 냉매의 압축시간을 증가시켜 냉방성능을 저하시킬 뿐만아니라, 전술한 바와 같은 이유로 발생한 진동은 NVH(Noise, vibration, and harshness)성능을 저하시키는 문제점이 있었다.Such a decrease in responsiveness not only decreases cooling performance by increasing the compression time of the refrigerant, but also causes vibration, which is caused by the aforementioned reasons, to deteriorate the noise, vibration, and harshness (NVH) performance.

아울러, 차량의 공조장치에 사용되는 가변 사판형 컴프레서는 항시 최고 성능(즉, 사판의 경사각이 최대로 기울여졌을 때)을 요구하지 않는다. 하지만, 경사각이 가변되는 구간에 있어 사판 경사각의 변화는 피스톤의 탑클리어런스(top clearance)를 증가시키며 이는 토출효율을 저하시킬 수 있었다. In addition, the variable swash plate type compressor used in the vehicle air conditioner does not always require the highest performance (that is, when the inclination angle of the swash plate is tilted to the maximum). However, in the section where the inclination angle is variable, the change of the swash plate inclination angle increases the top clearance of the piston, which may lower the discharge efficiency.

따라서, 본 발명은 상기와 같은 문제점을 해소하기 위하여 보다 신속한 응답성을 가지며 사판 경사각의 가변시에도 탑클리어런스의 증가를 억제하고 진동을 더욱 효율적으로 감쇠시킬 수 있는 가변 사판형 컴프레서를 제공하는 것에 주목적이 있다.
Accordingly, the present invention aims to provide a variable swash plate type compressor that can respond more quickly to the above problems and can suppress the increase of the top clearance and more effectively damp the vibration even when the swash plate tilt angle is variable. There is this.

상기와 같은 목적을 달성하기 위한 본 발명은, 축 회전하는 샤프트;와 상기 샤프트에 고정장착되며 로터암이 형성된 로터;와 일단이 상기 로터암에 연결되는 힌지핀; 및 샤프트에 끼워지는 허브와 결합되되, 상기 허브는 허브암을 갖고 상기 허브암에는 힌지핀의 타단이 연결되어 허브암의 회전위치에 따라서 샤프트와의 경사각이 가변가능하도록 회전하는 사판;을 포함하며, 상기 힌지핀의 양단은 로터암 및 허브암 각각에서 활주가능하도록 결합된 것을 특징으로 한다.The present invention for achieving the above object, the shaft is rotated; and a rotor fixedly mounted to the shaft and the rotor arm is formed; and a hinge pin one end is connected to the rotor arm; And a swash plate coupled to a hub fitted to the shaft, wherein the hub has a hub arm, and the hub arm is connected to the other end of a hinge pin, and the swash plate rotates so that the inclination angle with the shaft is variable according to the rotational position of the hub arm. Both ends of the hinge pin are slidably coupled to each of the rotor arm and the hub arm.

상기 로터암에는 장공(長孔)형 제1슬롯홀이 형성되고 상기 허브암에는 장공형 제2슬롯홀이 형성되되, 상기 힌지핀의 양단은 제1슬롯홀 및 제2슬롯홀 각각에 활주가능하도록 끼워지는 것을 특징으로 한다.A long slot-type first slot hole is formed in the rotor arm and a long slot-type second slot hole is formed in the hub arm, and both ends of the hinge pin are slidable in each of the first slot hole and the second slot hole. It is characterized in that it is fitted to.

그리고, 상기 로터암이 최상측에 위치하고 사판과 샤프트의 경사각이 직각을 이룰 때, 상기 힌지핀의 일단은 제1슬롯홀의 최하단에 위치하며 타단은 제2슬롯홀의 최상단에 위치하도록 구성된다.In addition, when the rotor arm is positioned at the top and the inclination angles of the swash plate and the shaft form a right angle, one end of the hinge pin is positioned at the bottom end of the first slot hole and the other end is positioned at the top end of the second slot hole.

본 발명의 다른 변형예로서, 상기 힌지핀에 의해 연결되는 로터암과 허브암은 짝을 이뤄 두 개 이상이 형성될 수도 있다.
As another variation of the present invention, two or more rotor arms and hub arms connected by the hinge pins may be formed in pairs.

상기와 같은 구성의 본 발명은 사판의 경사각에 따라 힌지핀이 보다 능동적으로 활주하여 컴프레서의 응답성을 향상시키며 언밸런스량을 감소시켜 진동을 더 효율적으로 감쇠시킬 수 있고 피스톤의 탑클리어런스가 축소되어 냉방성능을 더욱 향상시킬 수 있다.
According to the present invention, the hinge pin slides more actively according to the inclination angle of the swash plate, thereby improving the responsiveness of the compressor and reducing the unbalance amount, which can attenuate vibrations more efficiently. Performance can be further improved.

도 1a 는 종래의 가변 사판형 컴프레서에 장착되는 샤프트와 로터 및 사판이 결합된 모습을 촬영한 사진,
도 1b 는 종래의 구조에서 사판이 기울여질 때(윗쪽 도면)와 사판이 세워질 때(아랫쪽 도면)에 작용하는 힘과 모멘트를 표기한 도면,
도 2 는 본 발명의 바람직한 실시예에 따른 샤프트와 로터 및 사판이 결합된 모습을 도시한 측면도,
도 3 은 도 2 의 구조에서 샤프트의 회전시 작용하는 힘을 표기한 측면도,
도 4 는 종래의 구조와 본 발명의 구조에서 샤프트의 회전 시 각 구성요소들의 무게중심 변화를 비교하여 표시한 도면.Figure 1a is a photograph taken a state in which the shaft and the rotor and the swash plate coupled to a conventional variable swash plate type compressor,
Figure 1b is a view showing the forces and moments acting when the swash plate is tilted (upper view) and when the swash plate is erected (lower view) in the conventional structure,
Figure 2 is a side view showing a state in which the shaft and the rotor and the swash plate coupled according to a preferred embodiment of the present invention,
3 is a side view showing the force acting upon the rotation of the shaft in the structure of FIG.
Figure 4 is a view showing a comparison of the change in the center of gravity of each component during the rotation of the shaft in the structure of the conventional structure and the present invention.

이하, 도면을 참조하여 본 발명의 바람직한 실시예에 따른 가변 사판형 컴프레서를 더욱 상세히 설명한다.Hereinafter, a variable swash plate compressor according to a preferred embodiment of the present invention will be described in detail with reference to the accompanying drawings.

도 2 를 참조하면, 본 발명의 샤프트(40)는 엔진의 크랭크샤프트에 벨트 및 풀리를 통해 연결되어 축 회전하도록 구성된다. 상기 샤프트(40)에는 원판형 로터(30)와 사판(10)이 일정거리를 두고 나란하게 장착된다. 상기 로터(30)는 샤프트(40)에 고정장착되며 사판(10)을 향하는 면에 로터암(31)이 돌출된다. 상기 로터암(31)에는 장공형 제1슬롯홀(32)이 형성된다.2, the shaft 40 of the present invention is connected to the crankshaft of the engine via a belt and pulley is configured to axially rotate. The disk 40 and the swash plate 10 are mounted side by side at a predetermined distance to the shaft 40. The rotor 30 is fixedly mounted to the shaft 40 and the rotor arm 31 protrudes from the surface facing the swash plate 10. The rotor arm 31 is formed with a slot-type first slot hole 32.

상기 사판(10)은 허브(11)와 결합되어 샤프트(40)에 장착된다. 상기 허브(11)는 로터(30)를 향하는 면에 허브암(12)이 돌출되며 상기 허브암(12)에는 장공형 제2슬롯홀(13)이 형성된다. The swash plate 10 is coupled to the hub 11 and mounted on the shaft 40. The hub 11 has a hub arm 12 protruding from the surface facing the rotor 30, and the hub arm 12 has a long slot-shaped second slot hole 13.

그리고, 상기 제1슬롯홀(32)에는 힌지핀(20)의 일측이 활주가능하도록 결합되고, 제2슬롯홀(13)에는 힌지핀(20)의 타측이 활주가능하도록 결합된다.In addition, one side of the hinge pin 20 is slidably coupled to the first slot hole 32, and the other side of the hinge pin 20 is slidably coupled to the second slot hole 13.

상기 허브(11)는 사판(10)의 회전 및 (도면 상의) 좌우방향 움직임을 허용하도록 상기 사판(10)을 구속함으로서, 상기 사판(10)은 허브암(12)의 회전위치에 따라서 (샤프트와의) 경사각이 가변하며 피스톤(50)을 왕복운동시킨다. The hub 11 restrains the swash plate 10 to allow rotation of the swash plate 10 and horizontal movement (on the drawing), so that the swash plate 10 is in accordance with the rotational position of the hub arm 12 (shaft Angle of inclination is variable and reciprocates the piston 50.

본 발명의 바람직한 실시예에서는, (도 2 에 도시된 바와 같이) 상기 힌지핀(20)은, 로터암(31)이 최상측에 위치하고 사판(10)과 샤프트(40)의 경사각이 직각을 이룰 때(즉, 사판이 수직으로 세워졌을 때), 상기 힌지핀(20)의 일단은 제1슬롯홀(32)의 최하단에 위치하며 타단은 제2슬롯홀(13)의 최상단에 위치하도록 구성되며, 제1슬롯홀(32)은 (힌지핀이 제2슬롯홀에서도 활주 가능하므로 이를 상쇄하기 위하여) 종래의 슬롯홀 보다 더 짧은 길이를 갖도록 형성된다.In the preferred embodiment of the present invention (as shown in Figure 2), the hinge pin 20, the rotor arm 31 is located on the uppermost side and the inclination angle of the swash plate 10 and the shaft 40 is perpendicular to each other When (ie, when the swash plate is upright), one end of the hinge pin 20 is located at the bottom of the first slot hole 32 and the other end is located at the top of the second slot hole (13) In addition, the first slot hole 32 is formed to have a shorter length than the conventional slot hole (to offset the hinge pin is also slidable in the second slot hole).

한편, 본 발명의 다른 실시예로서 상기 힌지핀(20)에 의해 연결되는 로터암(31)과 허브암(12)은 짝을 이뤄 두 개 이상이 형성될 수도 있다.Meanwhile, as another embodiment of the present invention, two or more rotor arms 31 and hub arms 12 connected by the hinge pins 20 may be formed in pairs.

상기와 같이 구성된 본 발명은, 도 3 에 도시된 바와 같이 로터(30)의 회전에 따라서 힌지핀(20)이 제1슬롯홀(32)는 물론 제2슬롯홀(13)에서도 활주함으로써 사판(10)에 작용하는 합력의 방향과 힌지핀(20)의 활주방향의 차이를 종래 보다 감소시켜 초기응답성을 개선할 수 있다(즉, 도 1b 의 'A' 및 'B' 의 각도를 감소시킬 수 있다). 이때, 상기 제1슬롯홀(32)과 제2슬롯홀(13)의 길이 및 위치는 컴프레서의 용량 및 사판(10)의 크기에 따라 다르게 설정될 수 있다.According to the present invention configured as described above, as shown in FIG. 3, the hinge pin 20 slides in the second slot hole 13 as well as the first slot hole 32 according to the rotation of the rotor 30. 10, the difference between the direction of the force acting on the sliding direction and the sliding direction of the hinge pin 20 can be reduced than before, thereby improving the initial response (that is, reducing the angles of 'A' and 'B' of FIG. 1B). Can be). In this case, the length and position of the first slot hole 32 and the second slot hole 13 may be set differently according to the capacity of the compressor and the size of the swash plate 10.

도 4 를 참조하여, 본 발명의 구성과 종래의 구성을 더 상세히 비교하여 보면, 종래의 구조에서는 사판의 경사각이 가변되는 동안(즉, 사판이 샤프트에서 수직으로 세워진 위치에서 최대로 기울어지는 동안) 힌지핀의 무게 중심은 외측방향(즉, 무게 중심의 반대 방향)으로 이동하며, 허브의 무게 중심 또한 변경된다. 이러한 무게 중심 이동의 원인은, 회전축(샤프트)을 중심으로 허브 및 힌지핀의 위치이동이 발생하기 때문이며 이는 진동을 발생시키는 원인이 되었다.Referring to FIG. 4, in a more detailed comparison between the configuration of the present invention and the conventional configuration, while the inclination angle of the swash plate is varied in the conventional structure (that is, while the swash plate is maximally inclined at a position perpendicular to the shaft) The center of gravity of the hinge pin moves outward (ie opposite the center of gravity) and the center of gravity of the hub is also changed. The cause of the center of gravity movement is because the position movement of the hub and the hinge pin around the axis of rotation (shaft) occurs, which causes the vibration.

하지만, 본 발명에서는 사판(10)의 경사각이 가변되는 동안 힌지핀(20)의 (상측으로의) 이동량을 줄일 수 있으므로 무게 중심의 변화량을 감소시킬 수 있다.However, in the present invention, since the amount of movement of the hinge pin 20 (upward) can be reduced while the inclination angle of the swash plate 10 is variable, the amount of change in the center of gravity can be reduced.

따라서, 본 발명에서는 힌지핀(20)의 활주범위를 제한하지 않고 제1슬롯홀(32)을 축소시킴으로서(즉, 제1슬롯홀의 축소량 만큼 제2슬롯홀이 힌지핀의 활주범위를 보상할 수 있으므로) 힌지핀(20)의 무게중심 변화를 줄여 언밸런스량을 감소시킬 수 있고, 응답성을 향상시킬 수 있다.Accordingly, in the present invention, the first slot hole 32 is reduced without limiting the sliding range of the hinge pin 20 (that is, the second slot hole can compensate the sliding range of the hinge pin by the amount of reduction of the first slot hole. As a result, the unbalance amount can be reduced by reducing the change in the center of gravity of the hinge pin 20, and the response can be improved.

그러므로, 상기와 같은 본 발명의 구성에 따라서, 본 발명에서는 사판(10)의 경사각 변화가 더 원활히 이뤄짐으로서 경사각의 가변구간에서 피스톤(50)의 탑클리어런스를 감소시킬 수 있으며 이는 냉매의 압축효율을 개선할 수 있다.Therefore, according to the configuration of the present invention as described above, in the present invention, the change of the inclination angle of the swash plate 10 is made more smoothly, so that the top clearance of the piston 50 can be reduced in the variable section of the inclination angle, which reduces the compression efficiency of the refrigerant. It can be improved.

이상과 같이 본 명세서와 도면에 개시된 실시예들은 본 발명의 이해를 돕기 위해 특정 예를 제시한 것에 지나지 않으며, 본 발명의 범위를 제한하고자 하는 것은 아니다. 여기에 개시된 실시예들 이외에도 본 발명의 기술적 사상에 바탕을 둔 다른 변형예들이 실시 가능하다는 것은 본 발명이 속하는 기술분야에서 통상의 지식을 가진 자에게 자명한 것이다.
As described above, the embodiments disclosed in the present specification and drawings are only illustrative of specific examples in order to facilitate understanding of the present invention, and are not intended to limit the scope of the present invention. It will be apparent to those skilled in the art that other modifications based on the technical idea of the present invention are possible in addition to the embodiments disclosed herein.

10 : 사판
11 : 허브
12 : 허브암
13 : 제2슬롯홀
20 : 힌지핀
30 : 로터
31 : 로터암
32 : 제1슬롯홀
40 : 샤프트
50 : 피스톤10: swash plate
11: Hub
12: herb arm
13: second slot hole
20: hinge pin
30: rotor
31: rotor arm
32: first slot hole
40: Shaft
50: Piston

Claims (4)

축 회전하는 샤프트;와
상기 샤프트에 고정장착되며 로터암이 형성된 로터;와
일단이 상기 로터암에 연결되는 힌지핀; 및
샤프트에 끼워지는 허브와 결합되되, 상기 허브는 허브암을 갖고 상기 허브암에는 힌지핀의 타단이 연결되어 허브암의 회전위치에 따라서 샤프트와의 경사각이 가변가능하도록 회전하는 사판;을 포함하며,
상기 힌지핀의 양단은 로터암 및 허브암 각각에서 활주가능하도록 결합된 것을 특징으로 하는 가변 사판형 컴프레서.
Axial rotary shaft; and
A rotor fixed to the shaft and having a rotor arm; and
A hinge pin whose one end is connected to the rotor arm; And
It is coupled to the hub fitted to the shaft, the hub has a hub arm is connected to the other end of the hinge pin is connected to the hub arm is rotated so that the inclination angle with the shaft variable according to the rotational position of the hub arm; includes;
Both ends of the hinge pin is variable swash plate-type compressor, characterized in that coupled to the slide arm and the rotor arm respectively.
제 1 항에 있어서, 상기 로터암에는 장공형 제1슬롯홀이 형성되고 상기 허브암에는 장공형 제2슬롯홀이 형성되되,
상기 힌지핀의 양단은 제1슬롯홀 및 제2슬롯홀 각각에 활주가능하도록 끼워지는 것을 특징으로 하는 가변 사판형 컴프레서.
The method of claim 1, wherein the rotor arm is formed with a slot-type first slot hole and the hub arm is formed with a slot-type second slot hole,
And both ends of the hinge pin are slidably fitted into the first slot hole and the second slot hole, respectively.
제 2 항에 있어서, 상기 로터암이 최상측에 위치하고 사판과 샤프트의 경사각이 직각을 이룰 때, 상기 힌지핀의 일단은 제1슬롯홀의 최하단에 위치하며 타단은 제2슬롯홀의 최상단에 위치하도록 구성된 것을 특징으로 하는 가변 사판형 컴프레서.
According to claim 2, When the rotor arm is located at the top and the inclination angle of the swash plate and the shaft is at right angles, one end of the hinge pin is configured to be located at the bottom of the first slot hole and the other end is located at the top of the second slot hole Variable swash plate type compressor, characterized in that.
제 2 항에 있어서, 상기 힌지핀에 의해 연결되는 로터암과 허브암은 짝을 이뤄 두 개 이상이 형성되는 것을 특징으로 하는 가변 사판형 컴프레서.3. The variable swash plate compressor of claim 2, wherein two or more rotor arms and hub arms connected by the hinge pins are formed in pairs.
KR1020120126641A 2012-11-09 2012-11-09 Variable swash plate type compressor KR101345154B1 (en)

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Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010024892A (en) 2008-07-16 2010-02-04 Calsonic Kansei Corp Variable displacement compressor

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010024892A (en) 2008-07-16 2010-02-04 Calsonic Kansei Corp Variable displacement compressor

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