EP2067994B1 - Neigungsscheibenverdichter - Google Patents

Neigungsscheibenverdichter Download PDF

Info

Publication number
EP2067994B1
EP2067994B1 EP08021015A EP08021015A EP2067994B1 EP 2067994 B1 EP2067994 B1 EP 2067994B1 EP 08021015 A EP08021015 A EP 08021015A EP 08021015 A EP08021015 A EP 08021015A EP 2067994 B1 EP2067994 B1 EP 2067994B1
Authority
EP
European Patent Office
Prior art keywords
crank chamber
cavity
path
tilting plate
bearing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
EP08021015A
Other languages
English (en)
French (fr)
Other versions
EP2067994A3 (de
EP2067994A2 (de
Inventor
Masaki Kawachi
Yasuhiro Sakurai
Keigo Usui
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Marelli Corp
Original Assignee
Calsonic Kansei Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Calsonic Kansei Corp filed Critical Calsonic Kansei Corp
Publication of EP2067994A2 publication Critical patent/EP2067994A2/de
Publication of EP2067994A3 publication Critical patent/EP2067994A3/de
Application granted granted Critical
Publication of EP2067994B1 publication Critical patent/EP2067994B1/de
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/109—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • 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
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/123—Fluid connections

Definitions

  • the present invention relates to a tilting plate type compressor for reciprocating pistons by a swinging rotation of a tilting plate (swash plate, wobble plate).
  • the tilting plate type compressor 100 includes a housing 101.
  • the housing 101 is assembled primarily of a cylinder block 101a, a front head 101b provided at one end of the cylinder block 101a and a rear head 101c provided at another end of the cylinder block 101a via a valve plate 102.
  • a drive shaft 103 is provided at the center of the housing 101.
  • Bearing cavities 104 and 105 is formed near both ends of the drive shaft 103 within the front head 101b and the cylinder block 101a.
  • the bearing cavity 105 in the cylinder block 101a is configured of an inside cavity 105a opening into an after-mentioned crank chamber 112, a center cavity 105b having a smaller inner diameter and an outside cavity 105c provided on the side of the valve plate 102 as shown in Fig. 5 in detail.
  • a radial bearing 106 is provided within the bearing cavity 104 in the front head 101b.
  • Another radial bearing 107 is provided within the center cavity 105b of the bearing cavity 105 in the cylinder block 101a.
  • the drive shaft 103 is rotatably supported by the housing 101 via the bearings 106 and 107.
  • a thrust bearing 108 is provided within the outside cavity 105c of the bearing cavity 105.
  • the drive shaft 103 is supported in its axial direction by the thrust bearing 108.
  • cylinder bores 110 are formed on a circumference with the drive shaft 103 as the center.
  • a piston 111 capable of reciprocating is provided in each of the cylinder bores 110.
  • a crank chamber 112 is provided within the front head 101a, which communicates with the cylinder bores 110.
  • a rotor 113 fixed on an outer circumferential surface of the drive shaft 103
  • a sleeve 114 provided slidably on the outer circumferential surface of the drive shaft 103
  • a journal 116 provided outside the sleeve 114 and linked with the rotor 113 via a link 115 and a tilting plate 117 fixed on an outer circumferential surface of the journal 116.
  • the pistons 111 are coupled to an outer circumference of the tilting plate 117 via pairs of shoes 118.
  • First and second springs S1 and S2 are provided at both sides of the sleeve 114.
  • the tilting plate 117 will be returned to its initial position due to a balance between elastic forces of the first and second springs S1 and S2 after a shutdown.
  • the pistons 111 are reciprocated within the cylinder bores 110, respectively, due to the rotor 113, the tilting plate 117 and so on.
  • a reciprocating stroke amount of the pistons 111 is varied due to a tilted angle of the tilting plate 117.
  • a suction chamber 120 and a discharge chamber 121 are provided within the rear head 101c.
  • the valve plate 102 is interposed between the cylinder head 101a and the rear head 101c. Therefore, the cylinder bores 110 and the chambers 120 and 121 are partitioned by the valve plate 102.
  • an extraction path 122 communicating the crank chamber 112 with the suction chamber 120 and an intake path (not shown) communication the crank chamber 112 with the discharge chamber 121 are provided in the housing 101 and so on.
  • the extraction path 122 includes the inside cavity 105a and an intra-axis path 123 provided in the drive shaft 13 as its path.
  • the intra-axis path 123 is configured of a radial path 123a extending a radial direction of the drive shaft 103 and an axial path 123b extending an axial direction of the drive shaft 103 as shown in Fig. 5 in detail.
  • the tilting plate 117 swings to reciprocate the pistons 111 on the drive shaft 103 being rotated.
  • Refrigerant is supplied into the cylinder bore 110 from the suction chamber 120 during a suction stroke of the piston 111.
  • the supplied refrigerant is compressed and discharged into the discharge chamber 121 during a compression stroke of the piston 111.
  • the discharged refrigerant is circulated in a refrigerating cycle to be served for air-conditioning or the like and returned to the tilting plate type compressor 100.
  • a pressure in the crank chamber 112 is made low when thermal load for the refrigerating cycle becomes large during the tilting plate type compressor 100 driving.
  • a moment to increase a titled angle of the tilting plate 117 is applied to the tilting plate 117 and the journal 116 due to a pressure difference between a crank chamber pressure (a back pressure of the pistons 111) and a front pressure of the pistons 111.
  • the link 115 swings in an arrowed direction a in Fig. 4 due to the moment. Such swinging of the link 115 makes the tilted angle of the tilting plate 117 large.
  • the reciprocating stroke amount of the pistons 111 turns to be large when the tilted angle of the tilting plate 117 is made large. Thereby, a discharge amount of the refrigerant is made large, so that a cooling performance or the like is enhanced.
  • the pressure in the crank chamber 112 is made high when the thermal load for the refrigerating cycle becomes small.
  • a moment to decrease the tilted angle of the tilting plate 117 is applied to the tilting plate 117 and the journal 116 due to the pressure difference between the crank chamber pressure (the back pressure of the pistons 111) the front pressure of the pistons 111.
  • the link 115 swings in an arrowed direction b in Fig. 4 due to the moment. Such swinging of the link 115 makes the tilted angle of the tilting plate 117 small.
  • the reciprocating stroke amount of the pistons 111 turns to be small when the tilted angle of the tilting plate 117 is made small. Thereby, the discharge amount of the refrigerant is made small, so that the cooling performance or the like is reduced.
  • the tilting plate type compressor 100 conserves energy according to the above-mentioned operation.
  • the oil in the refrigerant flowing into the radial path 123a of the intra-axis path 123 is scattered toward the bearing cavity 105 by a centrifugal force due to the rotation of the drive shaft 103. This oil scattering prevents the oil contained in the refrigerant from flowing out of the crank chamber 120.
  • the oil scattered due to the centrifugal force of the drive shaft 103 attaches onto an inner surface of the bearing cavity 105 and stays therearound.
  • the oil may rush into the intra-axis path 123.
  • the oil may leak into the suction chamber 120 through the intra-axis path 123 finally.
  • an expanded recess 105d is provided on a circumferential surface of the bearing cavity 105 in order to supply the refrigerant into the bearing cavity 105 as much as possible.
  • the expanded recess 105d enlarges a space capacity for the oil staying and flowing-out of the oil through the intra-axis path 123 cannot be prevented by the expanded recess 105d.
  • the document EP 1 347 173 A2 discloses a tilting plate type compressor comprising a housing and a drive shaft rotatable supported by the housing via a bearing provided within a bearing cavity.
  • the housing includes a crank chamber and a plurality of cylinder bores that communicate with the crank chamber and in which a plurality of pistons are accommodated.
  • a tilting plate is provided within the crank chamber and is connected to the drive shaft to rotate therewith.
  • An extraction passage is provided that communicates between the crank chamber and a suction chamber. Said extraction passage includes an intra axis passage provided within the drive shaft and opens into the bearing cavity.
  • An intake passage is provided that communicates between the crank chamber and a discharge chamber.
  • An object of the present invention is to provide a tilting plate type compressor that can prevent oil from flowing-out from a crank chamber through an extraction path as much as possible.
  • An aspect of the present invention is to provide a capacity variable compressor that includes a housing within which a plurality of cylinder bores and a crank chamber communicating with the plurality of cylinder bores are provided; a drive shaft rotatably provided within the housing so as to penetrate the crank chamber and supported by the housing via a bearing provided within a bearing cavity; a tilting plate provided within the crank chamber and capable of swingably rotating due to a rotation of the drive shaft; a plurality of pistons capable of reciprocating within the plurality of cylinder bores, respectively, due to swingably rotating of the tilting plate; an extraction path communicating between the crank chamber and a suction chamber; and an intake path communicating between the crank chamber and a discharge chamber.
  • the extraction path includes an intra-axis path provided within the drive shaft and opens into the bearing cavity.
  • the intake path opens into the bearing cavity and communicates with the crank chamber via the bearing cavity.
  • oil had attached on an inner surface of the intra-axis path is sprayed outward due to a centrifugal force of the drive shaft and then attached on an inner surface of the bearing cavity and so on. Since the attached oil is returned to the crank chamber due to the refrigerant flowing to be inhaled into the crank chamber, oil leakage from the crank chamber can be prevented as much as possible.
  • an expanded cavity communicating with the bearing cavity is provided around the bearing cavity, and the intra-axis path opens into the expanded cavity.
  • the intake path opens into the bearing cavity (or the expanded cavity) at a farther position from the crank chamber than an opening position of the intra-axis path into the bearing cavity (or the expanded cavity).
  • the intake path opens at a lower position within the bearing cavity (or the expanded cavity) under an installed condition of the compressor.
  • oil had attached onto the inner surface of the bearing cavity (or the expanded cavity) may drop due to its weight and then stay at a lower area on the inner surface. Since the refrigerant to be inhaled flows into the crank chamber through the area where the oil stays, the returned oil amount to the crank chamber can be further increased.
  • a tilting plate type compressor 1 includes a housing 2.
  • the housing 2 is configured to be assembled of a cylinder block 2a, a front head 2b provided at one end of the cylinder block 2a and a rear head 2c provided at another end of the cylinder block 2a via a valve plate 3.
  • a drive shaft 4 is provided at the center of the housing 2. One end of the drive shaft 4 is projected outward from the front head 2b and a pulley 7 is fixed on the projected end to receive engine rotation. The drive shaft 4 is configured to rotate by receiving a drive force from the pulley 7 fixed on its one end.
  • Bearing cavities 30 and 31 is formed near both ends of the drive shaft 4 within the front head 2b and the cylinder block 2a.
  • the bearing cavity 31 in the cylinder block 2a is configured of an inside cavity 31a opening into an after-mentioned crank chamber 10, a center cavity 31b having a smaller inner diameter and an outside cavity 31c provided on the side of the valve plate 3 as shown in Fig. 2 in detail.
  • a radial bearing 5 is provided within the bearing cavity 30 in the front head 2b.
  • Another radial bearing 6 is provided within the center cavity 31b of the bearing cavity 31 in the cylinder block 2a.
  • the drive shaft 4 is rotatably supported by the housing 2 via the bearings 30 and 31.
  • a thrust bearing 32 and a disc spring 33 are provided within the inside cavity 31c of the bearing cavity 31.
  • the drive shaft 103 is supported in its axial direction by the thrust bearing 108.
  • the drive shaft 4 is pushed along its axial direction by an elastic force of the disc spring 33 to cancel its looseness along the axial direction and supported in the axial direction by the thrust bearing 32.
  • Cylinder bores 8 are formed within the cylinder block 2a.
  • the cylinder bores 8 are formed at even intervals on a circumference with the drive shaft 4 as the center.
  • a piston 9 capable of reciprocating is provided in each of the cylinder bores 8.
  • the crank chamber 10 is provided within the front head 2b, which communicates with the cylinder bores 8.
  • a rotor 11 fixed on an outer circumferential surface of the drive shaft 4
  • a sleeve 12 provided slidably on the outer circumferential surface of the drive shaft 4
  • a journal 13 provided outside the sleeve 12 and rotating along with the rotor 11, a tilting plate 15 fixed on an outer circumferential surface of the journal 13 and rear ends of the pistons 9, each coupled to an outer circumference of the tilting plate 15 via a pair of shoes 16.
  • An outer circumferential surface of the sleeve 12 is formed almost spherical to smoothly guide a transition of the tilted angle of the tilting plate 13.
  • First and second springs S1 and S2 are provided at both sides of the sleeve 12.
  • the tilting plate 15 will be returned to its initial position due to a balance between elastic forces of the first and second springs S1 and S2 after a shutdown.
  • the journal 13 and the rotor 11 are linked by a guide pin 13a which is fixed on the journal 13 and inserted into a guide hole 11a of the rotor 11.
  • each stroke of the pistons 9 is varied due to the tilted angle of the tilting plate 15 to change a discharge amount of refrigerant.
  • Mechanism for adjusting the tilted angle of the tilting plate 15 will be explained later.
  • a suction chamber 20 and a discharge chamber 21 for refrigerant gas are provided within the rear head 2c.
  • the suction chamber 20 is connected to an outlet of an evaporator in a refrigerating cycle via a suction port (not shown).
  • the discharge chamber 21 is connected to an inlet of a condenser in the refrigerating cycle via a discharge port (not shown).
  • the cylinder bores 8 and the chambers 20 and 21 are partitioned by the valve plate 3.
  • Discharge holes 24 are provided on the valve plate 3 within partitioning areas between the bores 8 and the discharge chamber 21.
  • a discharge valve is provided at each of the discharge holes 24.
  • Suction holes (not shown) are provided on the valve plate 3 within partitioning areas between the bores 8 and the suction chamber 20.
  • a suction valve (not shown) is provided at each of the suction holes.
  • an extraction path 25 is provided between the crank chamber 10 and the suction chamber 20, which is always opened.
  • An intake path 26 is provided between the crank chamber 10 and the discharge chamber 21.
  • a pressure control valve (not shown) is provided on the intake path 26. The pressure control valve is configured to control a pressure within the crank chamber 10 by adjusting its valve opening.
  • the extraction path 25 includes a bearing cavity 31, an intra-axis path 34 provided in the drive shaft 4, a hole formed on the valve plate 3 and a refrigerant path (not shown) provided in the rear head 2c as its path.
  • the intra-axis path 34 is configured of a radial path 34a extending a radial direction of the drive shaft 4 and an axial path 34b communicating with the radial path 34a and extending along an center axis of the drive shaft 4.
  • One end of the radial path 34a opens into an inside cavity 31a of the bearing cavity 31 and positioned at the middle of the thickness of the thrust bearing 32. Therefore, refrigerant to be extracted flows into the intra-axis path 34 through the interior of the thrust bearing 32.
  • One end of the axial path 34b opens into an outside cavity 31c of the bearing cavity 31.
  • the intake path 26 is configured of the bearing cavity 31, a first refrigerant path 27, a hole (not shown) provided on the valve plate 3 and a second refrigerant path (not shown).
  • the first refrigerant path 27 is provided in the cylinder block 2a and its one end opens into the bearing cavity 31.
  • the second refrigerant path is provided in the rear head 2c. One end of the second refrigerant path communicates with the hole and another end thereof opens into the discharge chamber 21.
  • the one end of the first refrigerant path 27 opens into the inside cavity 31a at a farther position from the crank chamber 10 than the opening position of the intra-axis path 34.
  • the one end of the first refrigerant path 27 opens at the lower position within the inside cavity 31a under an installed condition of the compressor 1.
  • the suction holes (not shown) are closed and the refrigerant gas within the cylinder bores 8 is compressed adiabatically by the pistons 9.
  • the compressed refrigerant gas with high-temperature and high-pressure is discharged from the discharge holes 24 to the discharge chamber 21.
  • the discharged refrigerant gas with high-temperature and high-pressure is discharged from the tilting plate type compressor 1 via the outlet port (not shown).
  • the discharged refrigerant gas is circulated in the refrigerating cycle to be served for air-conditioning or the like and returned to the tilting plate type compressor 1 again.
  • a supplying amount of the refrigerant into the crank chamber 10 through the intake path 26 is reduced by way of the pressure control valve (not shown) to reduce a pressure in the crank chamber 10 when thermal load for the refrigerating cycle becomes large during the tilting plate type compressor 1 driving.
  • the pressure control valve (not shown) to reduce a pressure in the crank chamber 10 when thermal load for the refrigerating cycle becomes large during the tilting plate type compressor 1 driving.
  • the supplying amount of the refrigerant into the crank chamber 10 through the intake path 26 is increased by way of the pressure control valve (not shown) to increase a pressure in the crank chamber 10 when the thermal load for the refrigerating cycle becomes small.
  • the balance will be disrupted between the counter-clockwise moment due to the crank chamber pressure (the back pressure of the pistons 9) and the elastic force of the first spring S1 and the clockwise moment due to the front pressure of the pistons 9 and the elastic force of the second spring S2.
  • the counter-clockwise moment becomes large to decrease the tilted angle of the tilting plate 15, so that the tilting plate 15 and the journal 13 swing in an arrowed direction b in Fig. 1 until the both moments are balanced.
  • the guide pin 13a is moved in the arrowed direction b from the large capacity state [ Fig. 1 ] toward the small capacity state.
  • Such swinging of the tilting plate 15 makes the tilted angle of the tilting plate 15 small.
  • the reciprocating stroke amount of the pistons 9 is made small when the tilted angle of the tilting plate 15 is made small. Thereby, the discharge amount of the refrigerant is made small, so that the cooling performance or the like is reduced.
  • the tilting plate type compressor 1 conserves energy according to the above-mentioned operation.
  • the refrigerant flowing into or from the crank chamber 10 during the tilting plate type compressor 1 driving flows into the suction chamber 20 with a lower pressure from the crank chamber 10 with a higher pressure through the extraction path 25.
  • the refrigerant to be extracted enters into the inside cavity 31a and then flows into the intra-axis path 34.
  • oil had attached on the inner surface of the intra-axis path 34 is sprayed outward due to a centrifugal force of the drive shaft 4 and then attached on the inner surface of the inside cavity 31a and so on.
  • the refrigerant to be inhaled flows into the crank chamber 10 through the intake path 26.
  • the refrigerant to be inhaled flows into the inside cavity 31a through the first refrigerant path 27 of the intake path 26 and then enters into the crank chamber 10 via the inside cavity 31a. Therefore, the above-mentioned oil on the inner surface of the inside cavity 31a is returned to the crank chamber 10 due to the inhaled refrigerant flowing. As a result, oil leakage from the crank chamber 10 can be prevented.
  • the refrigerant to be extracted supplies oil to the radial bearing 6 and the thrust bearing 32 by way of passing through the bearing cavity 31 as mentioned above.
  • the refrigerant to be extracted passing through the interior of the thrust bearing 32 and then flows into the intra-axis path 34, oil can be supplied to the thrust bearing 32 sufficiently.
  • the one end of the intake path 26 (the first refrigerant path 27) opens into the bearing cavity 31 (the inside cavity 31a) at a farther position from the crank chamber 10 than the opening position of the intra-axis path 34. Therefore, the refrigerant to be inhaled flows into the crank chamber 10 through an area, onto which oil had been scattered due to the centrifugal force of the drive shaft 4 and then on which the oil stays. As a result, returned oil amount to the crank chamber 10 can be increased.
  • the one end of the intake path 26 (the first refrigerant path 27) opens at the lower position within the bearing cavity 31 (the inside cavity 31a) under an installed condition of the compressor 1. Therefore, oil had attached onto the inner surface of the bearing cavity 31 may drop due to its weight and then stay at a lower area on the inner surface. Since the refrigerant to be inhaled flows into the crank chamber 10 through the area where the oil stays, the returned oil amount to the crank chamber 10 can be further increased.
  • FIG. 3 A modified embodiment is shown in Fig. 3 .
  • an expanded cavity 40 communicating with the inside cavity 31a is provided around the inside cavity 31a.
  • the intra-axis path 34 opens into the expanded cavity 40.
  • the expanded cavity 40 is provided along an entire circumference of the inside cavity 31a. Note that the expanded cavity 40 may be provided partially on the circumference of the inside cavity 31a (like the expanded recess 105d shown in Figs. 4 and 5 ).
  • the first refrigerant path 27 of the intake path 26 opens into the expanded cavity 40 at a farther position from the crank chamber 10 than an opening position of the intra-axis path 34.
  • one end of the first refrigerant path 27 opens at a lower position within the expanded cavity 40 under an installed condition of the compressor 1.
  • oil had attached on the inner surface of the bearing cavity 31 is returned to the crank chamber 10 due to the inhaled refrigerant flowing into the bearing cavity 31 from the intake path 26.
  • oil leakage from the crank chamber 10 can be prevented as much as possible.
  • the expanded cavity 40 communicating with the inside cavity 31a is provided around the inside cavity 31a and the intra-axis path 34 opens into the expanded cavity 40. Therefore, since oil is scattered toward not only the bearing cavity 31 but also the expanded cavity 40 due to the centrifugal force of the drive shaft 4, a space toward which oil is scattered can be increased. As a result, it can be prevented as much as possible that oil staying on the inner surface rushes into the intra-axis path 34 and leaks.
  • the intake path 26 opens into the expanded cavity 40 at a farther position from the crank chamber 10 than the opening position of the intra-axis path 34. Therefore, the refrigerant to be inhaled into the expanded cavity 40 flows into the crank chamber 10 through an area, onto which oil had been scattered due to the centrifugal force of the drive shaft 4 and then on which the oil stays. As a result, returned oil amount to the crank chamber 10 can be increased.
  • the one end of the intake path 26 (the first refrigerant path 27) opens at the lower position within the expanded cavity 40 under an installed condition of the compressor 1. Therefore, oil had attached onto the inner surface of the bearing cavity 31 may drop due to its weight and then stay at a lower area on the inner surface. Since the refrigerant to be inhaled into the expanded cavity 40 flows into the crank chamber 10 through the area where the oil stays, the returned oil amount to the crank chamber 10 can be further increased.
  • the refrigerant is extracted through the interior of the thrust bearing 32 to supply oil to the thrust bearing 32 sufficiently.
  • oil may be extracted through the interior of the radial bearing 6 to supply oil to the radial bearing 6 sufficiently.
  • oil may be extracted through both interiors of the trust bearing 32 and the radial bearing 6 to supply oil to the bearings 32 and 6 sufficiently.

Landscapes

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

Claims (6)

  1. Taumelscheiben-Kompressor (1), der umfasst:
    ein Gehäuse (2), in dem eine Vielzahl von Zylinderbohrungen (8) und eine Kurbelkammer (10) vorhanden sind, die mit der Vielzahl von Zylinderbohrungen (8) in Verbindung steht;
    eine Antriebswelle (4), die in dem Gehäuse (2) drehbar so vorhanden ist, dass sie durch die Kurbelkammer (10) hindurch verläuft, und die von dem Gehäuse (2) über ein Lager (32) getragen wird, das in einem Lager-Hohlraum (31) vorhanden ist, der sich in die Kurbelkammer (10) hinein öffnet;
    eine Taumelscheibe (15), die in der Kurbelkammer (10) vorhanden ist und sich aufgrund einer Drehung der Antriebswelle (4) schwingend drehen kann;
    eine Vielzahl von Kolben (9), die sich in der Vielzahl von Zylinderbohrungen (8) jeweils aufgrund schwingender Drehung der Taumelscheibe (15) hin- und herbewegen können;
    einen Ableitweg (25), der Verbindung zwischen der Kurbelkammer (10) und einer Ansaugkammer (20) herstellt; und
    einen Einlassweg (26), der separat von dem Ableitweg (25) vorhanden ist und Verbindung zwischen der Kurbelkammer (10) und einer Ablasskammer (21) herstellt, wobei der Ableitweg (25) einen inneraxialen Weg (34) enthält, der in der Antriebswelle (4) vorhanden ist und sich an einem äußeren Rand der Antriebswelle (34) in den Lager-Hohlraum (31) hinein öffnet,
    dadurch gekennzeichnet, dass
    sich der Einlassweg (26) in den Lager-Hohlraum (31) hinein öffnet, zu der Kurbelkammer (31) hin gerichtet ist und mit der Kurbelkammer (10) über den Lager-Hohlraum (31) in Verbindung steht.
  2. Kompressor (1) nach Anspruch 1, wobei
    ein erweiteter Hohlraum (40), der mit dem Lager-Hohlraum (31) in Verbindung steht, um den Lager-Hohlraum (31) herum vorhanden ist, und sich der inneraxiale Weg in den erweiterten Hohlraum hinein öffnet.
  3. Kompressor (1) nach Anspruch 1, wobei
    sich der Einlassweg (26) an einer Position in den Lager-Hohlraum (31) hinein öffnet, die weiter von der Kurbelkammer (10) entfernt ist als eine Öffnungsposition des inneraxialen Weges (34) in den Lager-Hohlraum (31) hinein.
  4. Kompressor (1) nach Anspruch 1 oder 3, wobei
    sich der Einlassweg (26) in einem installierten Zustand des Kompressors (1) an einer niedrigeren Position in den Lager-Hohlraum (31) hinein öffnet.
  5. Kompressor (1) nach Anspruch 2, wobei
    sich der Einlassweg (26) an einer Position in den erweiterten Hohlraum (40) hinein öffnet, die weiter von der Kurbelkammer (10) entfernt ist als eine Öffnungsposition des inneraxialen Weges (34) in den erweiterten Hohlraum (31) hinein.
  6. Kompressor (1) nach Anspruch 2 oder 5, wobei
    sich der Einlassweg (26) in einem installierten Zustand des Kompressors (1) an einer niedrigeren Position in den erweiterten Hohlraum (40) hinein öffnet.
EP08021015A 2007-12-06 2008-12-03 Neigungsscheibenverdichter Expired - Fee Related EP2067994B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2007315992A JP5140402B2 (ja) 2007-12-06 2007-12-06 斜板式コンプレッサ

Publications (3)

Publication Number Publication Date
EP2067994A2 EP2067994A2 (de) 2009-06-10
EP2067994A3 EP2067994A3 (de) 2011-05-11
EP2067994B1 true EP2067994B1 (de) 2012-06-20

Family

ID=40379661

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08021015A Expired - Fee Related EP2067994B1 (de) 2007-12-06 2008-12-03 Neigungsscheibenverdichter

Country Status (4)

Country Link
US (1) US20090145293A1 (de)
EP (1) EP2067994B1 (de)
JP (1) JP5140402B2 (de)
CN (1) CN101451518A (de)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8196506B2 (en) * 2009-08-17 2012-06-12 Delphi Technologies, Inc. Variable stroke compressor design
JP6032098B2 (ja) * 2013-03-29 2016-11-24 株式会社豊田自動織機 容量可変型斜板式圧縮機
KR20200086068A (ko) * 2019-01-08 2020-07-16 한온시스템 주식회사 압축기
JP7213700B2 (ja) * 2019-01-29 2023-01-27 サンデン株式会社 圧縮機
JP7213709B2 (ja) * 2019-02-06 2023-01-27 サンデン株式会社 圧縮機
KR20200105144A (ko) * 2019-02-28 2020-09-07 한온시스템 주식회사 압축기

Family Cites Families (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4061443A (en) * 1976-12-02 1977-12-06 General Motors Corporation Variable stroke compressor
US5584670A (en) * 1994-04-15 1996-12-17 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Piston type variable displacement compressor
US5836748A (en) * 1994-07-13 1998-11-17 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type variable displacement compressor utilizing a spool for controlling the inclination
JP4160669B2 (ja) * 1997-11-28 2008-10-01 株式会社不二工機 可変容量型圧縮機用制御弁
JP2000297746A (ja) * 1999-04-15 2000-10-24 Bosch Automotive Systems Corp 可変容量型斜板式クラッチレスコンプレッサ
DE19954570A1 (de) * 1999-11-12 2001-08-02 Zexel Valeo Compressor Europe Axialkolbenverdichter
DE10195089B4 (de) * 2000-11-23 2013-07-11 Ixetic Bad Homburg Gmbh Verdichter
DE10124033B4 (de) * 2001-05-16 2009-08-20 Daimler Ag Hubkolbenmaschine mit einer Schiebehülse
US6786703B2 (en) * 2001-11-02 2004-09-07 Delphi Technologies, Inc. Variable capacity air conditioning compressor with improved crankcase oil retention
JP4078229B2 (ja) * 2002-03-20 2008-04-23 カルソニックカンセイ株式会社 圧縮機
JP4118587B2 (ja) * 2002-04-09 2008-07-16 サンデン株式会社 可変容量圧縮機
DE60226781D1 (de) * 2002-05-14 2008-07-03 Zexel Valeo Climate Contr Corp Hubkolbenkompressor
US7364408B2 (en) * 2003-05-20 2008-04-29 Delphi Technologies, Inc. Crank case shut off valve
JP4483699B2 (ja) * 2005-01-27 2010-06-16 株式会社豊田自動織機 斜板式圧縮機
JP2006307700A (ja) * 2005-04-27 2006-11-09 Toyota Industries Corp 圧縮機
JP2007023937A (ja) * 2005-07-19 2007-02-01 Calsonic Kansei Corp 圧縮機
JP4630801B2 (ja) * 2005-11-04 2011-02-09 カルソニックカンセイ株式会社 圧縮機
JP4505482B2 (ja) * 2007-06-27 2010-07-21 カルソニックカンセイ株式会社 圧縮機
US20100143162A1 (en) * 2008-12-10 2010-06-10 Delphi Technologies, Inc. Suction shutoff valve

Also Published As

Publication number Publication date
JP5140402B2 (ja) 2013-02-06
US20090145293A1 (en) 2009-06-11
JP2009138631A (ja) 2009-06-25
EP2067994A3 (de) 2011-05-11
EP2067994A2 (de) 2009-06-10
CN101451518A (zh) 2009-06-10

Similar Documents

Publication Publication Date Title
EP2067994B1 (de) Neigungsscheibenverdichter
JP2002031050A (ja) 圧縮機
JP3790942B2 (ja) 斜板式圧縮機
KR20120090312A (ko) 가변용량형 사판식 압축기
KR20120065143A (ko) 가변용량형 사판식 압축기
JPH09242667A (ja) 往復動型圧縮機
JP2001355570A (ja) ピストン式容量可変型圧縮機
JP2004293388A (ja) 揺動斜板型ポンプ
JP2002138954A (ja) 回転斜板式圧縮機
EP2067993A2 (de) Verdichter mit variabler Leistung
WO2007086261A1 (ja) 可変容量型クラッチレス圧縮機
JP2007127084A (ja) 圧縮機
US6568312B2 (en) Thrust bearing structure for supporting a driving shaft of a variable displacement swash plate type compressor
JP2002005010A (ja) 可変容量圧縮機
EP1039128A2 (de) Schrägscheibenverdichter
JP4329053B2 (ja) 可変容量型斜板式圧縮機
EP1217211B1 (de) Fluidumverdrängungsmaschine
KR20150060199A (ko) 왕복식 압축기
JP2010024892A (ja) 可変容量コンプレッサ
KR100558704B1 (ko) 가변용량 사판식 압축기
JP4684166B2 (ja) 斜板式可変容量コンプレッサ
KR100715261B1 (ko) 가변 용량형 사판식 압축기
JP2009221968A (ja) コンプレッサ
KR20100031409A (ko) 사판식 압축기
JP2009138630A (ja) 可変容量コンプレッサ

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA MK RS

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA MK RS

17P Request for examination filed

Effective date: 20111111

AKX Designation fees paid

Designated state(s): DE FR GB

REG Reference to a national code

Ref country code: DE

Ref legal event code: R079

Ref document number: 602008016376

Country of ref document: DE

Free format text: PREVIOUS MAIN CLASS: F04B0027100000

Ipc: F04B0039120000

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RIC1 Information provided on ipc code assigned before grant

Ipc: F04B 39/10 20060101ALI20120201BHEP

Ipc: F04B 27/10 20060101ALI20120201BHEP

Ipc: F04B 39/12 20060101AFI20120201BHEP

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602008016376

Country of ref document: DE

Effective date: 20120823

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20121128

Year of fee payment: 5

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20121128

Year of fee payment: 5

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20130107

Year of fee payment: 5

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20130321

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602008016376

Country of ref document: DE

Effective date: 20130321

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 602008016376

Country of ref document: DE

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20131203

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20140829

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 602008016376

Country of ref document: DE

Effective date: 20140701

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140701

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20131203

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20131231