EP0220798A1 - Taumelscheibenverdichter mit Mechanismus zur Veränderung der Fördermenge - Google Patents

Taumelscheibenverdichter mit Mechanismus zur Veränderung der Fördermenge Download PDF

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Publication number
EP0220798A1
EP0220798A1 EP19860305956 EP86305956A EP0220798A1 EP 0220798 A1 EP0220798 A1 EP 0220798A1 EP 19860305956 EP19860305956 EP 19860305956 EP 86305956 A EP86305956 A EP 86305956A EP 0220798 A1 EP0220798 A1 EP 0220798A1
Authority
EP
European Patent Office
Prior art keywords
chamber
pressure
wobble plate
compressor
valve
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Withdrawn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
EP19860305956
Other languages
English (en)
French (fr)
Inventor
Yukihiko Taguchi
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.)
Sanden Corp
Original Assignee
Sanden 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 Sanden Corp filed Critical Sanden Corp
Publication of EP0220798A1 publication Critical patent/EP0220798A1/de
Withdrawn legal-status Critical Current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
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—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
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge chamber
    • 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
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1831—Valve-controlled fluid connection between crankcase and suction chamber
    • 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
    • F04B2027/1859—Suction pressure

Definitions

  • the present invention relates to a wobble plate type compressor and more particularly, to a wobble plate type compressor with a variable displacement mechanism suitable for use in an automobile air conditioning system.
  • a variable displacement mechanism is changed by varying the slant angle of the wobble plate to the drive shaft, i.e., the piston stroke of the pistons connected to the wobble plate is changed due to changes in the slant angle of wobble plate.
  • the volume of the compressor is changed in accordance with changes in the stroke of the piston.
  • the compressor 1 includes a compressor housing 2 having an annular casing 3, a cylinder block 4 which is attached to one end opening of the casing 3 and a cylinder head 5 which is attached to the other end surface of the cylinder block 4 via a valve plate 6.
  • An opening 21 is formed in the centre of the end of the casing 3 for a drive shaft 7 which is rotatably supported in the casing 3 by a bearing 18 disposed in the opening 21.
  • the inner end of the drive shaft 7 extends within a central bore 41 formed in the centre of the cylinder block 4 and rotatably supported by a bearing 19.
  • a rotor 8 is connected to the drive shaft 7 within the casing 3 and is engaged with an inclined plate 9 through a hinge portion 81, and the angle of the inclined plate 9 to the drive shaft 7 is changed by movememnt of the hinge portion 81.
  • a wobble plate 10 is disposed on the other side of the inclined plate 9 via a bearing 91.
  • a plurality of cylinders 13 are equiangularly formed in the cylinder block 4 and a piston is reciprocably disposed within each cylinder 13, connected to the wobble plate 10 by a respective connecting rod 11.
  • One end of the connecting rod 11 is connected to the wobble plate 10 with a ball joint and the other end of the connecting rod 11 is connected to the piston 12.
  • a guide bar 15 extends through the crank chamber 22 of the casing 3 and is fixed in the housing 2.
  • the lower end portion of the wobble plate 10 is engaged with the guide bar 15 to allow reciprocal motion of the wobble plate 10 while preventing rotational motion.
  • the cylinder head 5 is provided with a suction chamber 51 and a discharge chamber 52, which communicate with the cylinders 13 through suction holes 61 and discharge holes 62, respectively, formed through the valve plate 6.
  • a by-pass passage 42 is formed in the cylinder block 4 to accomplish communication between the discharge chamber 52 and the crank chamber 22 of the casing 3, and communication between the chambers is controlled by a valve mechanism 14 disposed in the cylinder head 5.
  • a by-pass passage 71 is formed in the drive shaft 7 to allow communication between the crank chamber 22 and the central bore 41, and the central bore 41 communicates with the suction chamber 51 through a passageway 43 formed in the cylinder block 4. Communication between the crank chamber 22 and the suction chamber 51 is also controlled by the valve mechanism 14.
  • the control valve mechanism 14 comprises a valve housing 141, bellows 142 containing a gas under a predetermined pressure and an operating pin 143 attached to the top of the bellows 142.
  • a valve housing 141 defines three chambers in a row; a first chamber 141a, a second chamber 141b, and a third chamber 141c.
  • the first chamber 141a communicates with the discharge chamber 52 through a first hole 141d and also communicates with the crank chamber 22 through a second hole 141e and the by-pass passage 42.
  • the second chamber 141b communicates with the interior of the crank chamber 22 through a third hole 141f, by-pass passage 71 and passageway 43, and also communicates with the suction chamber 51 through a fourth hole 141g.
  • the third chamber 141c in which the bellows 142 is disposed, communicates with the suction chamber 51 through a fifth hole 141h.
  • the operating pin 143 is slidably supported in a central portion 141i of the control valve mechanism 14 to extend through the three chambers, and is provided with a first valve portion 143a at one end and also a second valve portion 143b formed at the other end, to control the communication between the discharge chamber 52 and the crank chamber 22 and the suction chamber 51 and the crank chamber 22 respectively.
  • the drive shaft 7 is connected with a driving source, e.g., an engine of a car through the clutch.
  • a driving source e.g., an engine of a car
  • the inclined plate 9 is driven by the rotor 8 and the wobble plate 10 is wobbled back and forth by the movement of the inclined plate 9.
  • the piston 12 is thus reciprocated by the movement of the wobble plate 10 and, as a result of the reciprocating motion of the piston, refrigerant gas taken into the cylinders 13 from the suction chamber 51 is compressed and discharged to the discharge chamber 52.
  • the third chamber 141d of the valve mechanism 14 is normally connected to the suction chamber 51, if the pressure in suction chamber 51 is increased and the pressure in the third chamber 141d is higher than that of the gas in the bellows 142, the bellows 142 shrinks in accordance with the differential between the pressures. Accordingly, the operating pin 143 moves downwardly, and the first valve portion 143a of the operating pin 143 is positioned lower than the hole 141d. Therefore, the discharge chamber 52 is disconnected from the crank chamber 22 and, at the same time, since the second valve portion 143b also moves downwardly, the crank chamber 22 is connected with the suction chamber 51 through the second chamber 141b and holes 141f, 141g.
  • the pressure in the crank chamber 22, which acts on the rear of the pistons 12, is thus decreased, and the slant angle of wobble plate 10 to drive shaft 7 is increased due to the resulting increased stroke of the pistons 12.
  • the slant angle of the wobble plate 10 is at its largest angle, when the stroke of the pistons 12, i.e., the displacement of the compressor, is also at its maximum.
  • control valve mechanism 14 controls the slant angle of the wobble plate 10, i.e., the stroke of the pistons 12 is controlled in accordance with the pressure in the suction chamber 51 to maintain the pressure in the suction chamber 51. Accordingly, the pressure in the suction chamber 51 is substantially constant regardless of the rotational speed of the engine of the car.
  • the cooling performance may be decreased by the influence of the pressure loss in the refrigerant circuit between the outlet side of the evaporator and the compressor, when the heating load increases.
  • a wobble plate type compressor in accordance with the present invention includes a housing having a cylinder block provided with a plurality of cylinders; a suction chamber and a discharge chamber; a crank chamber adjacent the cylinder block; a piston slidable in each cylinder and arranged to be reciprocated by a drive mechanism including a wobble plate; an input drive rotor; and a drive shaft connected to the input rotor to drive the input rotor; slant angle control means having a control valve mechanism including a first valve to control the communication between the crank chamber and the discharge chamber, a second valve to control the communication between the crank chamber and the suction chamber, and a pressure sensing means to control operation of the first and second valves, chracterized in that the pressure sensing means is disposed within a pressure chamber unconnected with the suction chamber and having a port to which refrigerant pressure at a position in a refrigerant circuit between an inlet port of a compressor and an evaporator can be introduced in use.
  • the compressor 100 shown in Figure 4 is substantially of the same construction as the compressor 1 shown in Figure 1, except for the control valve mechanism, the same reference numerals are used to indicate the same parts of the compressor. The description of the construction and operation of the compressor except for the control valve mechanism will not be repeated in order to simplify the description.
  • the control valve mechanism 16 comprises a valve housing 161, a bellows 162 containing a gas under a predetermined pressure and an operating pin 163 attached to one end portion of the bellows 162.
  • a valve housing 161 is provided with three chambers; a first chamber 161a, a second chamber 161b and a third chamber 161c. These three chambers are formed in a row within the housing 161 and a pin 163 extends within the valve housing 161, extending through all three chambers.
  • the first chamber 161a is provided with a first hole 161d at its top to communicate with the discharge chamber 52 and is also provided with the second hole 161e at its periphery to communicate with the crank chamber 22 through a by-pass passage 42.
  • a ball valve element which comprises a ball 163a fixed on the end portion of the pin 163, a valve seat 164 and a spring 163b, is disposed within the chamber 161a to control the communication between the first hole 161d and the second hole 161e.
  • the spring 163b usually urges the ball 163b against the valve seat 164 to disconnect the first and second holes 161d, 161e.
  • the second chamber 161b is provided with a third hole 161f to communicate with the crank chamber 22 through the central bore 41 of the cylinder block 4 and the passageway 43, and is also provided with a fourth hole 161g to communicate with the suction chamber 51.
  • the throttle valve element which comprises a valve element 163c formed at the middle of the pin 163 and a valve seat 165 formed in an interior surface of the second chamber 161b, is disposed in the second chamber 161b to control communication between the third and fourth holes 161f and 161g.
  • the third chamber 161c is divided from the second chamber 161b by a partition plate 163j and is provided with a fifth hole 161h which connects the interior of the third chamber 161c and an accumulator 140 of the refrigerating system (see Fig. 5).
  • the outlet port of the compressor 100 is connected to a condenser 110.
  • An evaporator 130 is connected with the condenser 110 through an orifice 120, and the inlet port of the compressor 100 is connected with the evaporator 130 through an accumulator 140 which is also connected with the interior of the third chamber 161c of the control valve mechanism 16. The pressure in accumulator 140 is thus directly introduced into the interior of the third chamber 161c.
  • the bellows 162 shrinks due to the pressure difference between the third chamber 161c and the interior of the bellows 162. If the bellows 162 shrinks, the operating pin 163 moves downwardly and, at that time, the ball 163a of the operating pin 163 is pushed downwardly to contact the valve seat 164 thereby closing the communication between the first and second holes 161d, 161e. Thus, the discharge chamber 52 is disconnected from the crank chamber 22.
  • the throttle valve element 163c moves downward together with the operating pin 163 thereby to open the communication between the third and the fourth holes 161f, 161g.
  • the crank chamber 22 is thus connected with the suction chamber 51 through the holes 161f, 161g, the central bore 41, and the passageway 42, and as a result of this connection, the pressure in the crank chamber 22 and that on the rear of the pistons 12, decreases. Therefore, the slant angle of the wobble plate 10 to the drive shaft 7 is increased, the stroke of the piston 12 is increased and, thus, the compression capacity of the compressor 100 is increased. When the compression capacity of the compressor 100 is at its largest the pressure in suction chamber 51 is equal to the pressure in the crank chamber 22.
  • the bellows 162 when the pressure in the accumulator 140 is lower than a predetermined pressure in the bellows 162, the bellows 162 is expanded due to the pressure difference between the third chamber and the interior of the bellows 162 and when the bellows 162 expands, the operating pin 163 is moved upwardly, and the ball 163a is moved upwards against the recoil strength of the spring 163b to open communication between the first and the second holes 161d, 161e.
  • the discharge chamber 52 is connected with the crank chamber 22 through the first and second holes 161e, and the by-pass passage 42 and, as a result of this connection, the pressure in the crank chamber 22 is increased.
  • the throttle valve element 163c of the operating pin 163 moves upwards and contacts the valve seat 165 to close the communication between the third and fourth holes 161f, 161g. Therefore, the crank chamber 22 is disconnected from the suction chamber 51. If the pressure in the crank chamber 22 is increased, the slant angle of the wobble plate 10 to drive shaft 7 is decreased, the stroke of the piston 12 is decreased and, therefore the compression capacity of the compressor 100 is decreased.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP19860305956 1985-08-09 1986-08-01 Taumelscheibenverdichter mit Mechanismus zur Veränderung der Fördermenge Withdrawn EP0220798A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP12166985U JPS6231782U (de) 1985-08-09 1985-08-09
JP121669/85U 1985-08-09

Publications (1)

Publication Number Publication Date
EP0220798A1 true EP0220798A1 (de) 1987-05-06

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ID=14816964

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Application Number Title Priority Date Filing Date
EP19860305956 Withdrawn EP0220798A1 (de) 1985-08-09 1986-08-01 Taumelscheibenverdichter mit Mechanismus zur Veränderung der Fördermenge

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EP (1) EP0220798A1 (de)
JP (1) JPS6231782U (de)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3928162A1 (de) * 1988-08-26 1990-03-08 Toyoda Automatic Loom Works Kaeltemittel-taumelscheibenkompressor mit einem drucklager fuer die abstuetzung der taumelscheibe
US5000666A (en) * 1988-01-14 1991-03-19 Honda Giken Kogyo Kabushiki Kaisha Control device for variable displacement type compressor
US5145326A (en) * 1989-06-16 1992-09-08 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable capacity wobble plate type compressor with capacity regulating valve
US5486098A (en) * 1992-12-28 1996-01-23 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type variable displacement compressor
EP1033491A2 (de) * 1999-03-04 2000-09-06 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Befestigung eines Kontrollventils für einen variablen Verdrängungskompressor
EP1589223A1 (de) * 2003-01-22 2005-10-26 Zexel Valeo Climate Control Corporation Steuerventil für kompressor mit variabler verdrängung

Citations (4)

* 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
US4105370A (en) * 1977-05-19 1978-08-08 General Motors Corporation Variable displacement compressor with three-piece housing
US4108577A (en) * 1977-06-09 1978-08-22 General Motors Corporation Variable displacement compressor
EP0028453A1 (de) * 1979-10-31 1981-05-13 General Motors Corporation Führungsmechanismus für die Taumelscheibe eines Kompressors

Patent Citations (4)

* 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
US4105370A (en) * 1977-05-19 1978-08-08 General Motors Corporation Variable displacement compressor with three-piece housing
US4108577A (en) * 1977-06-09 1978-08-22 General Motors Corporation Variable displacement compressor
EP0028453A1 (de) * 1979-10-31 1981-05-13 General Motors Corporation Führungsmechanismus für die Taumelscheibe eines Kompressors

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5000666A (en) * 1988-01-14 1991-03-19 Honda Giken Kogyo Kabushiki Kaisha Control device for variable displacement type compressor
DE3928162A1 (de) * 1988-08-26 1990-03-08 Toyoda Automatic Loom Works Kaeltemittel-taumelscheibenkompressor mit einem drucklager fuer die abstuetzung der taumelscheibe
US4981419A (en) * 1988-08-26 1991-01-01 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Wobble plate type refrigerant compressor having a thrust bearing assembly for a wobble plate support
US5145326A (en) * 1989-06-16 1992-09-08 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable capacity wobble plate type compressor with capacity regulating valve
US5486098A (en) * 1992-12-28 1996-01-23 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type variable displacement compressor
EP1033491A2 (de) * 1999-03-04 2000-09-06 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Befestigung eines Kontrollventils für einen variablen Verdrängungskompressor
EP1033491A3 (de) * 1999-03-04 2001-01-03 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Befestigung eines Kontrollventils für einen variablen Verdrängungskompressor
US6254356B1 (en) 1999-03-04 2001-07-03 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Fitting structure for controlling valve in variable capacity compressor
EP1589223A1 (de) * 2003-01-22 2005-10-26 Zexel Valeo Climate Control Corporation Steuerventil für kompressor mit variabler verdrängung
EP1589223A4 (de) * 2003-01-22 2011-03-16 Valeo Thermal Sys Japan Co Steuerventil für kompressor mit variabler verdrängung

Also Published As

Publication number Publication date
JPS6231782U (de) 1987-02-25

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Inventor name: TAGUCHI, YUKIHIKO