WO2013179928A1 - 可変容量圧縮機 - Google Patents
可変容量圧縮機 Download PDFInfo
- Publication number
- WO2013179928A1 WO2013179928A1 PCT/JP2013/063917 JP2013063917W WO2013179928A1 WO 2013179928 A1 WO2013179928 A1 WO 2013179928A1 JP 2013063917 W JP2013063917 W JP 2013063917W WO 2013179928 A1 WO2013179928 A1 WO 2013179928A1
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- WO
- WIPO (PCT)
- Prior art keywords
- swash plate
- drive shaft
- arm
- variable capacity
- capacity compressor
- Prior art date
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Classifications
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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
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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
- F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
- F04B27/0895—Component parts, e.g. sealings; Manufacturing or assembly thereof driving means
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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
- F04B27/1054—Actuating elements
- F04B27/1063—Actuating-element bearing means or driving-axis bearing means
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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
- F04B27/1054—Actuating elements
- F04B27/1072—Pivot mechanisms
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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
- F04B2027/1809—Controlled pressure
- F04B2027/1813—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
- F04B27/14—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
- F04B2027/184—Valve controlling parameter
- F04B2027/1845—Crankcase pressure
Definitions
- the present invention relates to a variable capacity compressor, and more particularly to a variable capacity compressor used in a vehicle air conditioner system.
- Patent Document 1 discloses a technique for adding relative movement restriction means to stabilize the behavior of a swash plate with respect to a drive shaft.
- an object of the present invention is to provide a variable capacity compressor that can stabilize the behavior of a swash plate with a simple structure and can smoothly tilt the swash plate.
- a variable displacement compressor includes a housing in which a discharge chamber, a suction chamber, a crank chamber and a cylinder bore are formed, a piston disposed in the cylinder bore, and the housing A drive shaft that is rotatably supported by the motor, a rotor that rotates integrally with the drive shaft, a swash plate that rotates in synchronization with the rotation of the rotor connected via a connecting means, and the rotation of the swash plate.
- a conversion mechanism that converts the reciprocating motion of the piston, and a pressure control valve that can control the internal pressure of the crank chamber according to the opening,
- the opening degree is changed and the internal pressure of the crank chamber is changed, the inclination of the swash plate with respect to the drive shaft is changed while the swash plate is slid with the drive shaft to change the stroke of the piston.
- a variable capacity compressor configured to be capable of changing a discharge capacity when compressing the refrigerant sucked into the cylinder bore from the suction chamber and discharging the refrigerant into the discharge chamber,
- the coupling means directly or indirectly couples the first arm projecting from the rotor and the second arm projecting from the swash plate,
- the drive shaft is inserted eccentrically with respect to a through-hole drilled in the swash plate.
- the drive shaft is eccentric in the through hole and the side surface of the through hole and the outer peripheral surface of the drive shaft come into contact with each other, so that the swash plate tilts in the tilt change direction. Then, a frictional force acts between the through hole and the drive shaft, and it is avoided that the behavior of the swash plate becomes unstable due to this frictional force. According to this structure, a desired object can be achieved with almost no increase in cost.
- the drive shaft is inserted eccentrically toward the positive direction of rotation of the swash plate as viewed from the portion corresponding to the top dead center position.
- the drive shaft is eccentrically inserted into the through hole as viewed from the portion corresponding to the top dead center of the piston on the swash plate toward the positive direction side (compression process side) of the rotation of the swash plate.
- the through hole side surface on the positive direction side (compression process side) of the rotation of the swash plate and the outer peripheral surface of the drive shaft are in contact with each other. And the tilting of the swash plate in the tilt angle changing direction is prevented from being hindered by the frictional force.
- first arm and the second arm are connected by a connecting element, and the movable element is allowed by a gap formed between the connecting element and the first arm and between the connecting element and the second arm.
- the inclination of the swash plate fluctuates within the range, the inclination of the swash plate in the compression process side region closer to the positive direction of rotation of the swash plate than the portion corresponding to the top dead center position of the piston on the swash plate.
- the plate and the drive shaft are in contact with each other, and a clearance is secured between the swash plate and the drive shaft in the suction process side region closer to the negative direction of rotation of the swash plate than the portion corresponding to the top dead center position. It is preferred that According to such a configuration, it can be reliably avoided that the drive shaft hits diagonally at two points in the through-hole and the tilt of the swash plate in the tilt angle changing direction is inhibited.
- FIG. 1 It is a longitudinal section showing a variable capacity compressor concerning one embodiment of the present invention. It is a figure which shows the link arm of FIG. 1, (a) is a top view, (b) is the arrow view seen from the A direction of (a). It is a perspective view which shows the coupling body of the drive shaft and rotor of FIG. It is a perspective view which shows the swash plate of FIG. 1 shows the positional relationship among the rotor, drive shaft, link arm, and swash plate of FIG. 1, (a) is a plan view of a coupling body of the rotor and the drive shaft, (b) is a front view of the link arm, and (c) is an oblique view. It is a top view of a board. FIG.
- FIG. 6 is a partially enlarged schematic cross-sectional view in which a contact portion between the swash plate and the drive shaft of FIG. 5 is enlarged, (a) shows a state in which the through hole forming surface of the swash plate is parallel to the drive shaft, and (b) The through-hole formation surface of a swash plate shows the state inclined with respect to the drive shaft.
- variable capacity compressor according to the present invention includes a housing having a discharge chamber, a suction chamber, a crank chamber, and a cylinder bore formed therein, a piston disposed in the cylinder bore, and a rotatably supported in the housing.
- a control valve for adjusting the pressure of the crank chamber changing the pressure of the crank chamber by adjusting the opening of the control valve, changing the tilt angle of the swash plate, adjusting the stroke of the piston, Suck The variable displacement compressor which discharges into the discharge chamber from the chamber to compress the sucked refrigerant in the cylinder bore,
- the connecting means includes a first arm provided on the rotor and provided with a guide surface, a second arm provided on the swash plate, and a connecting element for connecting the first arm and the second arm.
- a plane T including the axis of the drive shaft and parallel to the guide surface of the first arm is perpendicular to the annular plane of the swash plate, and the outer periphery of the drive shaft is
- the connecting means is configured to be offset with respect to a plane U including the center of both side surfaces of the through-hole to be slidably supported and the top dead center position of the swash plate.
- the drive shaft is decentered in the through hole and the side surface of the through hole and the outer peripheral surface of the drive shaft come into contact with each other. Then, a frictional force acts between the through hole and the drive shaft, and it is avoided that the behavior of the swash plate becomes unstable due to this frictional force. According to this structure, a desired object can be achieved with almost no increase in cost.
- the swash plate is placed on the compression process side on a plane U that is orthogonal to the annular plane of the swash plate and includes the center of both side surfaces of the through hole that slides and supports the outer periphery of the drive shaft and the top dead center position of the swash plate.
- the direction in which the plane T is offset with respect to the plane U is preferably an area on the compression process side.
- the hole diameter (width in the left-right direction) of the through hole of the swash plate is set so that the outer peripheral surface of the drive shaft contacts the surface of the through hole on the compression process side only on one side. According to such a configuration, it is possible to reliably avoid the tilting of the swash plate in the angle change direction due to the drive shaft hitting diagonally at two points in the through hole.
- variable displacement compressor 100 shown in FIG. 1 is a clutchless compressor, and includes a cylinder block 101 having a plurality of cylinder bores 101a, and a front housing 102 provided at one end of the cylinder block 101.
- a cylinder head 104 is provided at the other end of the cylinder block 101 via a valve plate 103.
- a drive shaft 110 is provided across the crank chamber 140 defined by the cylinder block 101 and the front housing 102, and a swash plate 111 is disposed around the middle portion thereof.
- a through hole 111a through which the drive shaft 110 is inserted is formed in the swash plate 111.
- the through hole 111a has an inclination angle of the swash plate orthogonal to the annular plane of the swash plate 111, and the top dead center position and bottom dead center of the swash plate.
- the shape is formed so as to be tiltable in the range of the maximum inclination angle and the minimum inclination angle about the pivot axis K orthogonal to the plane including the point position.
- the top dead center position of the swash plate refers to a position where the compression process of the piston 136 ends
- the bottom dead center position refers to a position where the suction process of the piston 136 ends.
- the swash plate 111 is connected to a rotor 112 fixed to the drive shaft 110 via a link mechanism 120, and the inclination angle of the swash plate 111 can be changed while the side surface of the through hole 111a is slidably supported on the outer peripheral surface of the drive shaft 110. .
- the through hole 111a is formed with a minimum inclination angle restricting portion that comes into contact with the drive shaft 110.
- the minimum inclination restriction portion of the through hole 111a is formed so that the inclination angle of the swash plate is preferably 0 ° or more and less than 0.5 °.
- an inclination reduction spring 114 made of a compression coil spring that urges the swash plate 111 to the minimum inclination angle is mounted, and between the swash plate 111 and the spring support member 116, A tilt-increasing spring 115 comprising a compression coil spring that urges the swash plate 111 in a direction to increase the tilt angle to a predetermined tilt angle smaller than the maximum tilt angle is mounted. Since the biasing force of the tilt increasing spring 115 is set to be larger than the biasing force of the tilt decreasing spring 114 at the minimum tilt angle, when the drive shaft 110 is not rotating, the biasing force of the tilt decreasing spring 114 and the tilt increasing spring 115 are increased.
- the swash plate 111 is positioned so as to form a predetermined tilt angle at which the resultant force with the urging force becomes zero.
- One end of the drive shaft 110 extends through the boss portion 102a protruding to the outside of the front housing 102 and is connected to a power transmission device (not shown).
- a shaft seal device 130 is inserted between the drive shaft 110 and the boss portion 102a to shut off the inside and the outside.
- the drive shaft 110 and the rotor 112 are supported by bearings 131 and 132 in the radial direction, and supported by the bearing 133 and the thrust plate 134 in the thrust direction. Power from an external drive source is transmitted to the power transmission device, and the drive shaft 110 is driven. Is rotatable in synchronization with the rotation of the power transmission device.
- the gap between the contact portion of the drive shaft 110 with the thrust plate 134 and the thrust plate 134 is adjusted to a predetermined distance by the adjusting screw 135.
- a piston 136 is disposed in the cylinder bore 101 a, and the outer space of the swash plate 111 is accommodated in the inner space of the end of the piston 136 protruding toward the crank chamber 140, and the swash plate 111 is interposed via a pair of shoes 137.
- the piston 136 is linked to the structure. Therefore, the piston 136 can reciprocate in the cylinder bore 101a by the rotation of the swash plate 111.
- a suction chamber 141 and a discharge chamber 142 that annularly surrounds a radially outer portion of the suction chamber 141 are formed on the center side.
- the suction chamber 141 communicates with the cylinder bore 101a through a communication hole 103a provided in the valve plate 103 and a suction valve (not shown).
- the discharge chamber 142 communicates with the cylinder bore 101 a through a discharge valve (not shown) and a communication hole 103 b provided in the valve plate 103.
- the front housing 102, the cylinder block 101, the valve plate 103, and the cylinder head 104 are fastened by a plurality of through bolts 105 through a gasket (not shown) to form a compressor housing.
- a muffler is provided on the upper portion of the cylinder block 101, and the muffler is fastened by a bolt with a lid member 106 and a forming wall 101b formed on the upper portion of the cylinder block 101 via a seal member (not shown). It is formed by.
- a check valve 200 is disposed in the muffler space 143. The check valve 200 is disposed at a connection portion between the communication path 144 and the muffler space 143 and operates in response to a pressure difference between the communication path 144 (upstream side) and the muffler space 143 (downstream side).
- the communication path 144 When the pressure difference is smaller than the predetermined value, the communication path 144 is shut off, and when the pressure difference is larger than the predetermined value, the communication path 144 is opened.
- the discharge chamber 142 is connected to the discharge-side refrigerant circuit of the air conditioner system via the discharge passage formed by the communication passage 144, the check valve 200, the muffler space 143, and the discharge port 106a.
- the cylinder head 104 is formed with a suction port 104a and a communication passage 104b, and the suction chamber 141 is connected to a suction side refrigerant circuit of the air conditioner system through a suction passage formed by the communication passage 104b and the suction port 104a. .
- the suction passage extends linearly from the radially outer side of the cylinder head 104 so as to cross a part of the discharge chamber 142.
- the cylinder head 104 is further provided with a control valve 300.
- the control valve 300 controls the amount of discharge gas introduced into the crank chamber 140 by adjusting the opening of the communication passage 145 that communicates the discharge chamber 142 and the crank chamber 140.
- the refrigerant in the crank chamber 140 flows to the suction chamber 141 via the communication passage 101 c, the space 146, and the orifice 103 c formed in the valve plate 103.
- variable capacity compressor 100 it is possible to variably control the discharge capacity of the variable capacity compressor 100 by changing the pressure of the crank chamber 140 by the control valve 300 and changing the inclination angle of the swash plate 111 (that is, changing the stroke of the piston 136). it can.
- the air conditioner When the air conditioner is activated (that is, when the variable capacity compressor 100 is in an activated state), the energization amount to the solenoid built in the control valve 300 is adjusted based on the external signal, and the pressure in the suction chamber 141 is set to a predetermined value.
- the discharge capacity is variably controlled so that The control valve 300 can optimally control the suction pressure according to the external environment.
- the communication passage 145 is forcibly opened by turning off the energization to the solenoid built in the control valve 300 to be variable.
- the discharge capacity of the capacity compressor 100 can be controlled to the minimum.
- Link mechanism A rotor 112 is fixed to the drive shaft 110, and a pair of first arms 112a are projected from the rotor 112.
- One end side 121a of the link arm 121 formed in a substantially cylindrical shape is guided inside the pair of first arms 112a.
- a first connecting pin 122 as a connecting means into a through hole 112b formed in the first arm 112a and a through hole 121b formed in one end side 121a of the link arm 121, a link is established.
- the arm 121 is rotatable about the axis of the first connecting pin 122 while being guided by the pair of first arms 112a.
- the first connecting pin 122 is press-fitted and held in a through hole 121b formed in the link arm 121, and a small gap is formed between the outer periphery of the first connecting pin 122 and the through hole 112b formed in the first arm 112a. Is formed.
- the other end 121c of the link arm 121 is a pair of arms projecting from one end side 121a formed in a cylindrical shape, and a second arm 111b projecting from the swash plate 111 is guided inside thereof.
- a second connecting pin 123 as a connecting means into a through hole 121d formed in the other end side 121c of the link arm 121 and a through hole 111c formed in the second arm 111b, the link arm 121 is inserted.
- the swash plate 111 are connected, and the link arm 121 and the swash plate 111 are relatively rotatable about the axis of the second connecting pin 123.
- the second connecting pin 123 is press-fitted and held in the through hole 111c of the second arm 111b, and a minute gap is formed between the outer periphery of the second connecting pin 123 and the through hole 121d formed in the link arm 121. ing.
- the link mechanism 120 includes the first arm 112a, the second arm 111b, the link arm 121, the first connecting pin 122, and the second connecting pin 123. Accordingly, the swash plate 111 is connected to the rotor 112 fixed to the drive shaft 110 via the link mechanism 120, rotates by receiving the rotational torque of the rotor 112, and the inclination angle can be changed along the drive shaft 110. It has become.
- FIG. 5A shows a state where the coupling body of the drive shaft 110 and the rotor 112 is viewed from the swash plate 111 side.
- T is a plane T including the axis of the drive shaft 110 and parallel to the inner surface of the first arm 112a (the guide surface with which the one end side 121a of the link arm abuts).
- the pair of first arms 112a of the rotor 112 are arranged in parallel to the plane T, and the distance L1 between the guide surface on the one end side 121a of the link arm in the first arm 112a1 on the left side in the drawing and the plane T is the right side in the drawing.
- ⁇ L (L1 ⁇ L2) / Offset by two.
- ⁇ L is set in consideration of the gap between the outer diameter of the drive shaft 110 and the width of the through hole 111a in the plane V direction.
- the offset amount here refers to a case where at least ⁇ L> 0.1 mm.
- the center of the pair of first arms 112a and the center of the link arm 121 coincide with each other, and the guide surfaces of the pair of arms 121c with the second arm 111a are arranged symmetrically. ing.
- FIG. 5C shows a state where the swash plate 111 is viewed from the rotor 112 side.
- U is a plane U that is orthogonal to the annular plane P of the swash plate 111 and includes the top dead center position of the swash plate and the centers of both side surfaces of the through hole 111a
- V is the annular shape of the swash plate 111.
- the plane V includes a pivot K that is orthogonal to the plane P and orthogonal to the plane U.
- the upper side in the figure coincides with the top dead center position of the swash plate, and the lower side coincides with the bottom dead center position of the swash plate.
- the center of the second arm 111b coincides with the plane U.
- the plane U coincides with the center of the link arm 121 and the center of the pair of first arms 112a, the plane T is in the right direction in the drawing (on the compression process side) with respect to the centers of both side surfaces of the through hole 111a of the swash plate. Is offset by ⁇ L.
- the drive shaft 110 is eccentric to the compression process side in the through hole 111a.
- the link arm 121 is formed with a predetermined gap between the first arm 112a and the second arm 111b so that the link arm 121 rotates about the first connecting pin 122 and the second connecting pin 123, respectively. Yes. Then, when the link arm 121 and the second arm 111b are tilted in the left-right direction within the range of the clearance allowing displacement, as shown in FIG. 6B, the side surface on the compression process side of the through-hole 111a and the drive shaft
- the hole diameter of the through hole 111a (the width in the left-right direction in FIG. 5C) is set so that the outer peripheral surface of 110 is in contact with the contact part D and not in the diagonal part E of the contact part.
- the variable displacement compressor 100 when the variable displacement compressor 100 is operated and the piston 136 compresses the gas, the compression reaction force acts on the swash plate 111 via the piston 136, and the swash plate 111 is slightly tilted by the compression load.
- the side surface of the through-hole 111a on the compression process side and the outer peripheral surface of the drive shaft 110 come into contact with each other, so that when the swash plate 111 tries to tilt in the direction of bending, frictional force is generated between the through-hole 111a and the drive shaft 110.
- Due to the action of this frictional force the behavior of the swash plate 111 can be stabilized.
- the contact form between the through hole 111a and the drive shaft 110 is one side contact, the tilt of the swash plate 111 is remarkably inhibited by the drive shaft 110 being diagonally contacted at two points in the through hole 111a. Is prevented.
- the first arm of the rotor is offset, but the link arm or the second arm of the swash plate may be offset.
- the link mechanism is exemplified as the connecting means, but other hinge mechanisms (for example, as shown in Patent Document 1) may be used.
- the clutchless compressor is exemplified in the above-described embodiment
- the present invention is also applied to a variable displacement compressor equipped with an electromagnetic clutch, a swing plate type variable displacement compressor, and a variable displacement compressor driven by a motor.
- the invention can be applied.
- the present invention can be used as a variable capacity compressor for a vehicle air conditioner system or the like.
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- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
Description
前記開度が変更されて前記クランク室の内部圧力が変更されるとき、前記斜板を前記駆動軸と摺動させつつ前記斜板の前記駆動軸に対する傾角を変更して前記ピストンのストロークを変更することにより、前記吸入室から前記シリンダボアに吸入される冷媒を圧縮して前記吐出室に吐出する際の吐出容量を変更可能に構成される可変容量圧縮機であって、
前記連結手段は、前記ロータから突設された第1アームと、前記斜板から突設された第2アームとを直接的または間接的に連結しており、
前記駆動軸が、前記斜板に穿孔される貫通孔に対し偏心して挿通されていることを特徴とするものからなる。
前記連結手段は、前記ロータに設けられガイド面を備えた第1アームと、前記斜板に設けられた第2アームと、前記第1アームと前記第2アームとを連結する連結要素とを備え、
前記駆動軸と前記ロータの連結体において、前記駆動軸の軸線を含み第1アームのガイド面と平行な平面Tが、前記斜板において、円環状の平面と直交し、前記駆動軸の外周を摺動支持する前記貫通孔の両側面の中心と前記斜板の上死点位置とを含む平面Uに対してオフセットするように前記連結手段が構成されていることを特徴とするものからなる。
図1に示す可変容量圧縮機100はクラッチレス圧縮機であって、複数のシリンダボア101aを備えたシリンダブロック101と、シリンダブロック101の一端に設けられたフロントハウジング102と、シリンダブロック101の他端にバルブプレート103を介して設けられたシリンダヘッド104とを備えている。
駆動軸110にはロータ112が固定され、ロータ112には一対の第1アーム112aが突設されている。一対の第1アーム112aの内側に、ほぼ筒状に形成されたリンクアーム121の一端側121aがガイドされる。さらに、第1アーム112aに形成された貫通孔112bと、リンクアーム121の一端側121aに形成された貫通孔121bとの中に、連結手段としての第1連結ピン122を挿通することにより、リンクアーム121は、一対の第1アーム112aにガイドされながら第1連結ピン122の軸心を中心として回動可能となっている。尚、第1連結ピン122はリンクアーム121に形成された貫通孔121bに圧入保持され、第1連結ピン122の外周と第1アーム112aに形成された貫通孔112bとの間には微小な隙間が形成されている。
図5(a)は駆動軸110とロータ112の連結体を斜板111側から見た状態を示したものである。図中Tは、駆動軸110の軸線を含み第1アーム112aの内側の面(リンクアームの一端側121aが当接するガイド面)と平行な平面Tである。ロータ112の一対の第1アーム112aは平面Tに平行に配置され、図中左側の第1アーム112a1におけるリンクアームの一端側121aのガイド面と平面Tとの距離L1は、図中右側の第1アーム112a2におけるリンクアームの一端側121aのガイド面と平面Tとの距離L2より僅かに大きくなっている。つまり、一対の第1アーム112aのガイド面は平面Tに対して対称ではなく、一対の第1アーム112aのガイド面の中心は平面Tに対して図中左側にΔL=(L1-L2)/2だけオフセットしている。尚、ΔLは駆動軸110の外径と貫通孔111aの平面V方向の幅との隙間を考慮して設定されるが、ここで言うオフセット量とは少なくともΔL>0.1mmの場合を指す。
101 シリンダブロック
101a シリンダボア
101b 形成壁
101c 連通路
102 フロントハウジング
102a ボス部
103 バルブプレート
103a、103b 連通孔
104 シリンダヘッド
104a 吸入ポート
104b 連通路
105 通しボルト
106 蓋部材
106a 吐出ポート
110 駆動軸
111 斜板
111a 貫通孔
111b 第2アーム
111c 貫通孔
112 ロータ
112a、112a1、112a2 第1アーム
112b 貫通孔
114 傾角減少バネ
115 傾角増大バネ
116 バネ支持部材
120 リンク機構
121 リンクアーム
121a リンクアームの一端側
121b 貫通孔
121c リンクアームの他端側
121d 貫通孔
122 第1連結ピン
123 第2連結ピン
130 軸封装置
131、132、133 軸受
134 スラストプレート
135 調整ネジ
136 ピストン
137 シュー
140 クランク室
141 吸入室
142 吐出室
143 マフラ空間
144、145 連通路
146 空間
200 逆止弁
300 制御弁
D 接触部位
E 接触部位の対角側部位
P、T、U、V 平面
Claims (3)
- 内部に吐出室、吸入室、クランク室およびシリンダボアが形成されたハウジングと、前記シリンダボア内に配設されたピストンと、前記ハウジングに回転可能に支持される駆動軸と、前記駆動軸と一体に回転するロータと、連結手段を介して連結された前記ロータの回転に同期して回転する斜板と、該斜板の回転をピストンの往復運動に変換する変換機構と、開度に応じて前記クランク室の内部圧力を制御可能な圧力制御弁とを備え、
前記開度が変更されて前記クランク室の内部圧力が変更されるとき、前記斜板を前記駆動軸と摺動させつつ前記斜板の前記駆動軸に対する傾角を変更して前記ピストンのストロークを変更することにより、前記吸入室から前記シリンダボアに吸入される冷媒を圧縮して前記吐出室に吐出する際の吐出容量を変更可能に構成される可変容量圧縮機であって、
前記連結手段は、前記ロータから突設された第1アームと、前記斜板から突設された第2アームとを直接的または間接的に連結しており、
前記駆動軸が、前記斜板に穿孔される貫通孔に対し偏心して挿通されていることを特徴とする可変容量圧縮機。 - 前記駆動軸が、前記上死点位置に対応する部位からみて前記斜板の回転の正方向寄りに偏心して挿通されている、請求項1に記載の可変容量圧縮機。
- 第1アームと第2アームとが連結要素で連結されており、前記連結要素と第1アームとの間および前記連結要素と第2アームとの間で形成される隙間により許容される可動範囲内で前記斜板の傾きが変動したときに、前記斜板上の前記ピストンの上死点位置に対応する部位よりも前記斜板の回転の正方向寄りの圧縮工程側領域において前記斜板と前記駆動軸とが接触し、前記上死点位置に対応する部位よりも前記斜板の回転の負方向寄りの吸入工程側領域において前記斜板と前記駆動軸との間に隙間が確保される、請求項2に記載の可変容量圧縮機。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
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US14/402,499 US20150132153A1 (en) | 2012-05-28 | 2013-05-20 | Variable Displacement Compressor |
DE112013002688.0T DE112013002688B4 (de) | 2012-05-28 | 2013-05-20 | Verdichter mit variabler Verdrängung mit einer exzentrischen Durchführung der Antriebswelle durch die Taumelscheibe |
CN201380027516.9A CN104471245B (zh) | 2012-05-28 | 2013-05-20 | 容量可变型压缩机 |
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JP2012120953A JP6047307B2 (ja) | 2012-05-28 | 2012-05-28 | 可変容量圧縮機 |
JP2012-120953 | 2012-05-28 |
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WO2013179928A1 true WO2013179928A1 (ja) | 2013-12-05 |
Family
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PCT/JP2013/063917 WO2013179928A1 (ja) | 2012-05-28 | 2013-05-20 | 可変容量圧縮機 |
Country Status (5)
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US (1) | US20150132153A1 (ja) |
JP (1) | JP6047307B2 (ja) |
CN (1) | CN104471245B (ja) |
DE (1) | DE112013002688B4 (ja) |
WO (1) | WO2013179928A1 (ja) |
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JP6194830B2 (ja) * | 2014-03-24 | 2017-09-13 | 株式会社豊田自動織機 | 容量可変型斜板式圧縮機 |
Citations (4)
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JPH08338362A (ja) * | 1995-06-08 | 1996-12-24 | Toyota Autom Loom Works Ltd | 可変容量型斜板式圧縮機 |
JP2002257036A (ja) * | 2001-02-16 | 2002-09-11 | Halla Aircon Co Ltd | 斜板の加工方法及びこれを用いた斜板式可変容量圧縮機 |
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JP2007120394A (ja) * | 2005-10-27 | 2007-05-17 | Calsonic Kansei Corp | 可変容量圧縮機 |
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KR910004933A (ko) * | 1989-08-09 | 1991-03-29 | 미다 가쓰시게 | 가변용량사판식 압축기 |
JPH11264371A (ja) * | 1998-03-18 | 1999-09-28 | Toyota Autom Loom Works Ltd | 可変容量型圧縮機 |
JP4035922B2 (ja) * | 1999-04-02 | 2008-01-23 | 株式会社豊田自動織機 | 容量可変型圧縮機 |
EP1126165A1 (en) * | 1999-08-20 | 2001-08-22 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Variable displacement swash plate type compressor |
JP2002364530A (ja) | 2001-06-06 | 2002-12-18 | Toyota Industries Corp | 可変容量圧縮機 |
DE102004028747A1 (de) | 2004-06-14 | 2005-12-29 | Obrist Engineering Gmbh | Hubkolbenkompressor |
JP4751166B2 (ja) * | 2005-10-12 | 2011-08-17 | カルソニックカンセイ株式会社 | 可変容量圧縮機 |
JP4976731B2 (ja) * | 2006-04-07 | 2012-07-18 | カルソニックカンセイ株式会社 | 可変容量圧縮機 |
KR100903037B1 (ko) * | 2007-10-19 | 2009-06-18 | 학교법인 두원학원 | 용량가변형 사판식 압축기 |
JP5123715B2 (ja) * | 2008-04-07 | 2013-01-23 | カルソニックカンセイ株式会社 | 斜板式圧縮機 |
-
2012
- 2012-05-28 JP JP2012120953A patent/JP6047307B2/ja active Active
-
2013
- 2013-05-20 US US14/402,499 patent/US20150132153A1/en not_active Abandoned
- 2013-05-20 WO PCT/JP2013/063917 patent/WO2013179928A1/ja active Application Filing
- 2013-05-20 DE DE112013002688.0T patent/DE112013002688B4/de active Active
- 2013-05-20 CN CN201380027516.9A patent/CN104471245B/zh active Active
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JPH08338362A (ja) * | 1995-06-08 | 1996-12-24 | Toyota Autom Loom Works Ltd | 可変容量型斜板式圧縮機 |
JP2002257036A (ja) * | 2001-02-16 | 2002-09-11 | Halla Aircon Co Ltd | 斜板の加工方法及びこれを用いた斜板式可変容量圧縮機 |
JP2003262185A (ja) * | 2002-03-07 | 2003-09-19 | Toyota Industries Corp | 可変容量型斜板式圧縮機 |
JP2007120394A (ja) * | 2005-10-27 | 2007-05-17 | Calsonic Kansei Corp | 可変容量圧縮機 |
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DE112013002688B4 (de) | 2018-07-12 |
JP2013245631A (ja) | 2013-12-09 |
DE112013002688T5 (de) | 2015-02-19 |
JP6047307B2 (ja) | 2016-12-21 |
CN104471245B (zh) | 2016-10-26 |
US20150132153A1 (en) | 2015-05-14 |
CN104471245A (zh) | 2015-03-25 |
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