EP1164290A2 - Compresseur à plateau en biais - Google Patents

Compresseur à plateau en biais Download PDF

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Publication number
EP1164290A2
EP1164290A2 EP01114207A EP01114207A EP1164290A2 EP 1164290 A2 EP1164290 A2 EP 1164290A2 EP 01114207 A EP01114207 A EP 01114207A EP 01114207 A EP01114207 A EP 01114207A EP 1164290 A2 EP1164290 A2 EP 1164290A2
Authority
EP
European Patent Office
Prior art keywords
crank chamber
crank
refrigerant
swash plate
piston
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.)
Withdrawn
Application number
EP01114207A
Other languages
German (de)
English (en)
Other versions
EP1164290A3 (fr
Inventor
Naoya Yokomachi
Kiyoshi Yagi
Tatsuya Koide
Junya Suzuki
Toshiro Fujii
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.)
Toyota Industries Corp
Original Assignee
Toyota Industries 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 Toyota Industries Corp filed Critical Toyota Industries Corp
Publication of EP1164290A2 publication Critical patent/EP1164290A2/fr
Publication of EP1164290A3 publication Critical patent/EP1164290A3/fr
Withdrawn legal-status Critical Current

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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

Definitions

  • the present invention relates to a piston type variable displacement compressor.
  • the present invention relates to a piston type variable displacement compressor having a characteristic lubrication structure in its crank chamber.
  • a piston type variable displacement compressor includes: a drive shaft rotated by an external drive source; and a piston for sucking, compressing and discharging refrigerant according to a rotational motion of the drive shaft.
  • a rotational motion of the drive shaft is transformed into a reciprocating motion of the piston by a crank mechanism provided in a crank chamber.
  • This crank mechanism functions as a variable displacement mechanism for changing a stroke of the piston according to the inner pressure in the crank chamber.
  • This crank mechanism is composed of a plurality of parts, and a large number of sliding sections, in which the parts slide on each other, are arranged in the crank mechanism. In order to operate the crank mechanism smoothly, it is necessary to ensure a smooth sliding motion in each sliding section.
  • a lubricant sucking passage for connecting this communicating passage with an oil reservoir section in the crank chamber.
  • the lubricant is sucked up by the pressure of the refrigerant gas, which passes through this communicating passage from the high pressure region to the crank chamber, from the oil reservoir section via the lubricant sucking passage.
  • the thus sucked lubricant is atomized in the crank chamber.
  • a hinge mechanism for changing an inclination angle of a swash plate This hinge mechanism is arranged on the opposite side to the cylinder block with respect to the swash plate. In this structure, the lubricant is atomized on the cylinder block side of the swash plate.
  • the above structure disclosed in the above unexamined patent publication has the following disadvantages. Since the communicating passage is formed in the cylinder block, it must be formed between the cylinder bores which are composed in the cylinder block. In this structure, the hinge mechanism is arranged on the opposite side to the cylinder block with respect to the swash plate. Therefore, it is difficult for the lubricant, which has been atomized in the communicating passage, to reach the hinge mechanism. Further, in this structure, an outlet for the refrigerant gas in the communicating passage is arranged at a position lower than the drive shaft. Therefore, it is very difficult to spread the lubricant all over the crank chamber. Especially when a flow rate of the refrigerant gas passing in the communicating passage is low, the above disadvantages become remarkable.
  • the present invention provides a piston type variable displacement compressor comprising: a crank chamber defined in a housing; and a crank mechanism, arranged in the crank chamber, for transforming a rotational motion of a drive shaft into a reciprocating motion of a piston which sucks, compresses and discharges refrigerant and also for changing a stroke of the piston according to an inner pressure in the crank chamber, wherein an outlet of a gas supply passage for supplying the refrigerant from a high pressure region into the crank chamber is open at an upper position of the crank mechanism in the crank chamber.
  • the degree of freedom in designing the arrangement of the outlet can be increased as compared with an arrangement in which the outlet is open to the cylinder block. Therefore, the above structure is very effective in the case where parts, which require complete lubrication, such as parts receiving high intensity compressive reaction forces from the piston, are arranged separate from the cylinder block.
  • the above outlet is open at an upper position of the crank mechanism, the mist-like lubricant mixed in the refrigerant easily spreads all over the crank chamber, so that the crank chamber can be excellently lubricated, especially, the crank mechanism can be effectively lubricated.
  • the upper portion of the crank mechanism is defined as a region on the upper side of the horizontal face passing through the drive shaft except for the crank mechanism.
  • Fig. 1 is a cross-sectional view showing an outline of a piston type variable displacement compressor of an embodiment of the present invention.
  • Fig. 1 the upper side of Fig. 1 is defined as upper, and the left of Fig. 1 is defined as front.
  • a compressor C includes: a cylinder block 1; a front housing 2 joined to the front end of the cylinder block 1; and a rear housing 4 joined to the rear end of the cylinder block 1 via a valve forming body 3.
  • These cylinder block 1, front housing 2, valve forming body 3 and rear housing 4 are joined and fixed to each other by a plurality of through-bolts 10 (Only one through-bolt 10 is shown in Fig. 1.), so that the housing of compressor C is completed.
  • a crank chamber 5 In a region surrounded by the cylinder block 1 and the front housing 2, there is defined a crank chamber 5.
  • the drive shaft 6 is rotatably supported by a pair of radial bearings 8A, 8B which are respectively arranged in the front and the rear portion of the drive shaft 6.
  • a spring 7 In an accommodation recess formed at the center of the cylinder block 1, there are provided a spring 7 and a rear thrust bearing 9B.
  • the lug plate 11 is fixed to the drive shaft 6 in the crank chamber 5 in such a manner that the lug plate 11 can be rotated integrally with the drive shaft 6.
  • the front side thrust bearing 9A is arranged between the lug plate 11 and the inner wall face of the front housing 2.
  • the drive shaft 6 and the lug plate 11, which are integrated with each other, are positioned in the direction of thrust (the axial direction of the drive shaft) by the rear thrust bearing 9B, which is pushed to the front side by a spring 7, and the front thrust bearing 9A.
  • the front end portion of the drive shaft 6 is connected with a vehicle engine E, which is an external drive source, via a power transmission PT.
  • the power transmission PT may be a clutch mechanism (for example, an electromagnetic clutch) by which power can be transmitted and/or shut off by electrically controlling the clutch mechanism from outside.
  • the power transmission PT may be a clutchless mechanism (for example, a combination of a belt with a pulley) having no clutch mechanism, by which power can be transmitted at all times.
  • the clutchless type power transmission mechanism is adopted.
  • a swash plate 12 which is a cam plate.
  • a through-hole is formed at the center of the swash plate 12.
  • the drive shaft 6 is arranged penetrating this through-hole formed at the center of the swash plate 12.
  • the swash plate 12 is connected with the lug plate 11 and the drive shaft 6 via the hinge mechanism 13.
  • the hinge mechanism 13 includes: two support arms 14 (Only one support arm is shown in the drawing.) protruding from the rear face of the lug plate 11; and two guide pins 15 (Only one guide pin is shown in the drawing.) protruding from the front face of the swash plate 12.
  • the swash plate 12 can be simultaneously rotated with the lug plate 11 and the drive shaft 6, and further the swash plate 12 can be tilted with respect to the drive shaft 6 while the swash plate 12 is being slid in the axial direction of the drive shaft 6.
  • an inclination angle reducing spring 16 which is arranged round the drive shaft 6. This inclination angle reducing spring 16 pushes the swash plate 12 in a direction so that the swash plate 12 can approach the cylinder block 1, that is, the inclination angle can be reduced.
  • a restriction ring 18, which is fixed to the drive shaft 6, and the swash plate 12 there is provided a return spring 17 which is arranged around the drive shaft 6.
  • the inclination angle of the swash plate 12 is defined as an angle formed between a virtual plane, which is perpendicular to the drive shaft 6, and the swash plate 12.
  • each cylinder bore 1a there are provided a plurality of cylinder bores 1a (Only one cylinder bore is shown in the drawing.) which are arranged round the drive shaft 6. An end on the rear side of each cylinder bore 1a is closed by the valve forming body 3.
  • a single-headed type piston 20 capable of reciprocating.
  • a compression chamber In each cylinder bore 1a, there is provided a compression chamber, the volume of which is changed according to the reciprocating motion of the piston 20.
  • the front end portion of each piston 20 is engaged with the outer peripheral portion of the swash plate 12 via a pair of shoes 19.
  • Each piston 20 is connected with the swash plate 12 via these shoes 19.
  • a crank mechanism is composed in which the front side thrust bearing 9A, lug plate 11, swash plate 12, support arm 14, guide pin 15 and shoes 19 convert the rotational motion of the drive shaft 6 into the reciprocating motion of the piston 20 and at the same time the stroke of the piston 20 is changed.
  • the valve forming body 3 is composed of a suction valve forming plate, port forming plate, discharge valve forming plate and retainer forming plate which are put on each other.
  • a suction port 23 corresponding to each cylinder bore 1a, there are provided a suction port 23, suction valve 24 for opening and closing the suction port 23, discharge port 25 and discharge valve 26 for opening and closing the discharge port 25.
  • the suction chamber 21 and each cylinder bore 1a are communicated with each other via the suction port 23.
  • Each cylinder bore 1a and the discharge chamber 22 are communicated with each other via the discharge port 25.
  • the suction chamber 21 and the crank chamber 5 are connected with each other by the gas extraction passage 27 formed so that the cylinder block 1 and the valve forming body 3 can be penetrated by the gas extraction passage 27.
  • the discharge chamber 22 and crank chamber 5 are connected with each other by the gas supply passage 28.
  • the gas supply passage 28 is formed in the peripheral wall section of the housing.
  • the outlet 28A which is an opening on the crank chamber 5 side, is open to an upper portion of the crank mechanism in the above peripheral wall section.
  • the control valve 29 adjusts the degree of opening of the gas supply passage 28 according to a signal sent from a control computer not shown in the drawing.
  • a quantity of high pressure gas introduced into the crank chamber 5 via the gas supply passage 28 and a quantity of gas introduced out from the crank chamber 5 via the gas extraction passage 27 are controlled so that both the quantities can be appropriately balanced.
  • crank pressure Pc inner pressure in the crank chamber
  • crank chamber pressure Pc a difference between crank pressure Pc via the piston 20 and the inner pressure in the cylinder bore 1a is changed, so that an inclination angle of the swash plate 12 is changed.
  • the stroke of the piston 20 can be changed, that is, the discharge capacity can be changed.
  • the suction chamber 21 and the discharge chamber 22 are connected with each other by the external refrigerant circuit 30.
  • the external refrigerant circuit 30 includes a condenser 31, expansion valve 32 and evaporator 33.
  • the external refrigerant circuit 30 and the compressor C compose a refrigerating circuit of the vehicle air-conditioner.
  • mist-like lubricant is mixed in the refrigerant gas flowing in the compressor C. Sliding portions of the movable parts provided in the compressor C can be lubricated by this mist-like lubricant.
  • each piston 20 is reciprocated by a stroke corresponding to the inclination angle of the swash plate 12, so that the refrigerant can be repeatedly sucked, compressed and discharged in each cylinder bore 1a in this order.
  • the refrigerant gas supplied from the external refrigerant circuit 30 into the suction chamber 21 is sucked into the cylinder bore 1a via the suction port 23 and compressed by the piston 20 when the piston 20 is moved. After that, the refrigerant gas is discharged into the discharge chamber 22 via the discharge port 25, so that it is sent out into the external refrigerant circuit 30.
  • the control valve 29 is adjusted so that the degree of opening of the gas supply passage 28 can be decreased. Due to the foregoing, a quantity of high pressure refrigerant gas supplied from the discharge chamber 22 into the crank chamber 5 via the gas supply passage 28 is decreased. Therefore, the pressure in the crank chamber 5 is reduced, and the inclination angle of the swash plate 12 is increased. Accordingly, the discharge capacity of compressor C can be increased. When the gas supply passage 28 is completely closed, the pressure in the crank chamber 5 is greatly reduced, and the inclination angle of the swash plate 12 is increased to the maximum. Accordingly, the discharge capacity of the compressor C becomes maximum.
  • the control valve 29 is adjusted so that the degree of opening of the gas supply passage 28 can be increased. Due to the foregoing, the pressure in the crank chamber 5 is raised, and the inclination angle of the swash plate 12 is decreased. Accordingly, the discharge capacity of the compressor C is reduced. When the gas supply passage 28 is completely opened, the pressure in the crank chamber 5 is greatly raised, and the inclination angle of the swash plate 12 is decreased to the minimum. Accordingly, the discharge capacity of the compressor C becomes minimum.
  • the refrigerant gas sent from the gas supply passage 28 is supplied to the crank chamber 5 from an upper portion of the crank mechanism via the outlet 28A. At this time, mist-like lubricant mixed in the refrigerant gas is also supplied from the outlet 28A into the crank chamber 5. Therefore, the crank mechanism is mainly lubricated, and also sliding portions of the movable parts in the crank chamber 5 and sliding portions of the movable parts on the cylinder block 1 side are lubricated.
  • the gas supply passage 28 including the outlet 28A is arranged in the peripheral wall section of the compressor housing. Due to the foregoing, the degree of freedom of the arrangement of the outlet 28A can be enhanced. For example, compared with a case in which the gas supply passage 28 is formed so that it can penetrate the cylinder block 1 and the valve forming body 3 and in which the outlet 28A is arranged so that it can be opened to the cylinder block 1, it becomes easy to arrange that the outlet 28A can be opened to the opposite side to the cylinder block 1 with respect to the swash plate 12.
  • a reaction force given to the piston 20 in the case of compression mainly acts in a direction so that the crank mechanism and the drive shaft 6 can be pushed to the front side of the compressor C.
  • the front side thrust bearing 9A and the hinge mechanism 13 mainly receive the reaction force.
  • the outlet 28A is arranged in the peripheral wall section of the compressor housing, it becomes possible to arrange the outlet 28A at a position where the front side thrust bearing 9A and the hinge mechanism 13, which are arranged on the opposite side to the cylinder block 1 with respect to the swash plate 12, can be effectively lubricated.
  • the compressor C can be smoothly operated and the life of the compressor C can be extended. Since the above effect can be provided by the simple structure in which the outlet 28A is arranged in the peripheral wall section of the compressor housing, it is possible to expect that the manufacturing cost can be reduced.
  • the outlet 28A is open to an upper portion of the crank mechanism in the peripheral wall section of the housing of the compressor C. Due to the above structure, the mist-like lubricant can be easily spread all over the crank chamber 5. Accordingly, the crank chamber 5 can be excellently lubricated. Especially, the crank mechanism can be effectively lubricated. For example, even when a quantity of the refrigerant supplied to the crank chamber 5 via the gas supply passage 28 is small, a quantity of the lubricant supplied to the crank mechanism can be relatively increased because the lubricant is supplied from the upper portion of the crank mechanism.
  • a state in which a quantity of the refrigerant supplied to the crank case 5 via the gas supply passage 28 is small is caused not only by a case in which the degree of opening of the gas supply passage 28 is adjusted to be small by the control valve 29 but also by a case in which a small inclination angle of the swash plate 12 (a small discharge capacity) is kept over a long period of time.
  • the reason is described as follows. When operation is continued over a long period of time under the condition that the discharge capacity is small, the inner pressure in the discharge chamber 22 is gradually lowered, so that a difference between the inner pressure in the discharge chamber 22 and crank chamber pressure Pc becomes small.
  • this state in which the discharge capacity is small is kept over a long period of time such as a period in which no operation is conducted in winter. Therefore, in a state in which the discharge capacity is small, a great advantage can be provided by the enhancement of the lubrication efficiency.
  • the control valve 29 is provided in the gas supply passage 28. Due to the foregoing, the gas supply passage 28 can be also used as a pressure adjusting hole for adjusting the inner pressure in the crank chamber 5 by the control valve 29. Accordingly, it becomes unnecessary to form the pressure adjusting hole differently from the gas supply passage 28. Accordingly, the structure can be made simple.
  • the compressor C may be of a type in which a wobble plate and a drive shaft 6 are not integrally rotated, for example, the compressor C may be of the wobble type.
  • control valve 29 may be arranged in the gas extraction passage 27. According to this arrangement, when the control valve adjusts the degree of opening of the gas extraction passage 27, a quantity of the refrigerant introduced out from the crank chamber 5 via the gas extraction passage 27 and a quantity of refrigerant introduced in via the gas supply passage 28 are controlled so that they can be balanced. In this way, the crank chamber pressure Pc can be changed.
  • the type of control may not be an external control type in which the degree of opening of the control valve 29 is adjusted by the control conducted from the outside, but the type of control may be an internal control type in which the degree of opening of the control valve 29 is adjusted by the independent control of the control valve itself.
  • the control valve 29 of the external control type it is preferable to use the control valve 29 of the external control type.
  • the piston type variable displacement compressor of the present invention may be any of the compressor in which the swash plate and the drive shaft are integrally rotated and the compressor in which the swash plate and the drive shaft are not integrally rotated.
  • the crank chamber can be excellently lubricated by a simple structure in any operating condition.
  • the aforementioned outlet 28A may be formed toward the thrust bearing for supporting the crank mechanism in the axial direction of the drive shaft and/or the hinge mechanism for changing a stroke of the piston.
  • the thrust bearing and the hinge mechanism can be effectively lubricated.
  • a gas extraction passage for introducing the refrigerant from the crank chamber into the low pressure region may be provided, and a control valve for changing a quantity of the refrigerant introduced from the crank chamber into the low pressure region may be provided in this gas extraction passage.
  • the gas extraction passage can be also used as a pressure adjusting hole for adjusting the inner pressure in the crank chamber by the control valve.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)
EP01114207A 2000-06-14 2001-06-12 Compresseur à plateau en biais Withdrawn EP1164290A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2000178397 2000-06-14
JP2000178397A JP2001355570A (ja) 2000-06-14 2000-06-14 ピストン式容量可変型圧縮機

Publications (2)

Publication Number Publication Date
EP1164290A2 true EP1164290A2 (fr) 2001-12-19
EP1164290A3 EP1164290A3 (fr) 2003-07-02

Family

ID=18679831

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01114207A Withdrawn EP1164290A3 (fr) 2000-06-14 2001-06-12 Compresseur à plateau en biais

Country Status (3)

Country Link
US (1) US20010053327A1 (fr)
EP (1) EP1164290A3 (fr)
JP (1) JP2001355570A (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004003386A1 (fr) * 2002-06-27 2004-01-08 Luk Fahrzeug-Hydraulik Gmbh & Co.Kg Compresseur
EP1411243A1 (fr) * 2002-10-18 2004-04-21 TGK CO., Ltd. Soupape de commande pour un compresseur à capacité variable
US7520210B2 (en) 2006-09-27 2009-04-21 Visteon Global Technologies, Inc. Oil separator for a fluid displacement apparatus
CN101725498B (zh) * 2008-10-28 2012-10-24 株式会社丰田自动织机 具有排量控制机构的可变排量式压缩机

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7013021B2 (en) * 1999-03-19 2006-03-14 Digimarc Corporation Watermark detection utilizing regions with higher probability of success
JP2008045523A (ja) * 2006-08-21 2008-02-28 Toyota Industries Corp 可変容量型圧縮機における容量制御構造
JP4345807B2 (ja) 2006-12-13 2009-10-14 株式会社豊田自動織機 可変容量型圧縮機における容量制御構造
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

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10299647A (ja) 1997-04-22 1998-11-10 Sanden Corp 潤滑機構付き圧縮機

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5765886A (en) * 1980-10-06 1982-04-21 Diesel Kiki Co Ltd Rotary swash-plate type compressor
JPH09250452A (ja) * 1996-03-19 1997-09-22 Toyota Autom Loom Works Ltd 圧縮機における潤滑構造
JPH10196540A (ja) * 1997-01-10 1998-07-31 Toyota Autom Loom Works Ltd 圧縮機

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10299647A (ja) 1997-04-22 1998-11-10 Sanden Corp 潤滑機構付き圧縮機

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004003386A1 (fr) * 2002-06-27 2004-01-08 Luk Fahrzeug-Hydraulik Gmbh & Co.Kg Compresseur
FR2845430A1 (fr) * 2002-06-27 2004-04-09 Luk Fahrzeug Hydraulik Compresseur
EP1411243A1 (fr) * 2002-10-18 2004-04-21 TGK CO., Ltd. Soupape de commande pour un compresseur à capacité variable
US7520210B2 (en) 2006-09-27 2009-04-21 Visteon Global Technologies, Inc. Oil separator for a fluid displacement apparatus
CN101725498B (zh) * 2008-10-28 2012-10-24 株式会社丰田自动织机 具有排量控制机构的可变排量式压缩机

Also Published As

Publication number Publication date
JP2001355570A (ja) 2001-12-26
US20010053327A1 (en) 2001-12-20
EP1164290A3 (fr) 2003-07-02

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