WO1999066203A1 - Compresseur sans embrayage du type a plateau oscillant a deplacement variable - Google Patents

Compresseur sans embrayage du type a plateau oscillant a deplacement variable Download PDF

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Publication number
WO1999066203A1
WO1999066203A1 PCT/JP1999/003203 JP9903203W WO9966203A1 WO 1999066203 A1 WO1999066203 A1 WO 1999066203A1 JP 9903203 W JP9903203 W JP 9903203W WO 9966203 A1 WO9966203 A1 WO 9966203A1
Authority
WO
WIPO (PCT)
Prior art keywords
passage
discharge
chamber
swash plate
pressure
Prior art date
Application number
PCT/JP1999/003203
Other languages
English (en)
Japanese (ja)
Inventor
Yukio Kazahaya
Shoichi Kido
Original Assignee
Bosch Automotive Systems Corporation
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 Bosch Automotive Systems Corporation filed Critical Bosch Automotive Systems Corporation
Priority to EP99925334A priority Critical patent/EP1088991A1/fr
Publication of WO1999066203A1 publication Critical patent/WO1999066203A1/fr

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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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
    • 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
    • F04B2027/185—Discharge 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
    • F04B2027/1854—External parameters
    • 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
    • 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
    • F04B2027/1863—Controlled by crankcase pressure with an auxiliary valve, controlled by
    • F04B2027/1872—Discharge pressure

Definitions

  • the present invention relates to a variable-capacity swash plate type clutchless compressor to which, for example, the driving force of an engine is constantly transmitted, and in particular, to prevent a high-pressure refrigerant from flowing out to a condenser at an extremely low load, thereby allowing the refrigerant to flow inside the compressor.
  • the present invention relates to a variable capacity swash plate type clutchless compressor that circulates and reduces the refrigeration capacity to zero.
  • variable-capacity swash plate type clutchless compressor as a conventional clutchless compressor.
  • the inclination angle of the swash plate changes according to the suction pressure, the stroke of the stone changes, and the discharge rate increases or decreases.
  • variable displacement swash plate type clutchless compressor that does not have a minimum discharge capacity of zero is used as the clutchless compressor
  • the heat load decreases (the compressor with a clutch).
  • the cooling of the evaporator is caused by the refrigerant, the frost forms on the surface of the evaporator, and the evaporator freezes, making it difficult to ventilate. May be impaired.
  • the heat load is reduced Note that the inclination angle of the swash plate decreases, and the swash plate pushes the transmission cylinder toward the rear side, and the transmission cylinder pushes the blocking body toward the rear side.
  • the shut-off body closes the suction passage, preventing the inflow of low-pressure refrigerant gas from the evaporator.
  • the control valve communicates the discharge chamber with the crank chamber, and the high-pressure refrigerant gas in the discharge chamber flows to the crank chamber, and the refrigerant gas hardly flows to the capacitor side.
  • the discharge chamber must be located outside the suction chamber in the cylinder head. No stricter seal management with outside air. For example, higher processing accuracy and an appropriate tightening amount of the port (bolt for connecting the cylinder block and the head) are required.
  • An object of the present invention is to provide a variable-capacity swash plate type clutchless compressor that facilitates management of seals against outside air, suppresses noise, and further improves reliability. And Disclosure of the invention
  • a variable-capacity swash plate type clutchless compressor is mounted on a rotating shaft so as to be slidable and tiltable, and rotates integrally with the rotating shaft.
  • a crank chamber for accommodating the swash plate, a suction chamber for accommodating a refrigerant gas to be sent to the compression chamber, and a refrigerant gas in the crank chamber guided to the suction chamber, and the inclination angle of the swash plate A first passage whose passage cross-sectional area is reduced by the swash plate when the pressure is minimum, a discharge chamber for accommodating the refrigerant gas discharged from the compression chamber, and a condenser for discharging the refrigerant gas from the discharge chamber.
  • the discharge control valve is a check valve.
  • a first orifice is formed in the middle of the third passage, and a passage area of the first orifice is increased by a second orifice formed in the middle of the first passage. It is preferred that it be smaller than the passage area of the access.
  • the function of introducing the refrigerant gas from the crank chamber to the suction chamber through the third passage only when the passage cross-sectional area of the first passage is reduced by the swash plate is simplified. It can be realized with a configuration.
  • Variable capacity type swash plate type clutchle according to a second aspect of the present invention
  • the compressor is slidably and tiltably mounted on the rotating shaft, and is configured to rotate integrally with the rotating shaft, a crank chamber accommodating the swash plate, and a suction chamber accommodating refrigerant gas to be sent to the compression chamber.
  • a discharge chamber for containing the refrigerant gas discharged from the compression chamber, a discharge port for sending the refrigerant gas from the discharge chamber to the capacitor side, and a discharge gas for guiding the refrigerant gas of the discharge chamber to the discharge port A passage, a second passage for guiding the refrigerant gas from the discharge chamber to the crank chamber, and a passage provided in the middle of the second passage, wherein the second passage is shut off when the heat load increases.
  • a pressure control valve on the second passage is
  • a pressure reducing means provided in the flow to reduce the flow of the refrigerant gas guided to the crank chamber; and a pressure of the refrigerant gas downstream of the pressure control valve and upstream of the pressure reducing means, and an urging force of an urging member. Acts in the valve closing direction, and the pressure in the discharge chamber acts in the valve opening direction, so that the pressure of the refrigerant gas downstream of the pressure control valve and upstream of the pressure reducing means and the discharge pressure
  • a discharge control valve that shuts off the discharge passage when the pressure difference in the room becomes equal to or less than a predetermined value; and a refrigerant gas in the crank chamber only when the discharge control valve shuts off the discharge passage.
  • the response of the discharge control valve is improved, and the discharge control valve can be quickly operated.
  • the amount of refrigerant discharged (the capacity of the compressor) can be changed, and cooling filling is improved.
  • the discharge control valve operates reliably and the refrigeration capacity can be reduced to zero. Therefore, in order to ensure the operation of the discharge control valve, it is not necessary to set the passage cross-sectional area of the first passage small and set the pressure in the crank chamber high. Therefore, the damage to the components in the crank chamber is reduced, and the durability and reliability of the compressor are improved.
  • the pressure reducing means is a third orifice located downstream of the pressure control valve.
  • the flow rate of the refrigerant gas is reduced by the third orifice, the pressure of the refrigerant gas supplied to the crank chamber is reduced, and Link chamber pressure is not too high.
  • a fourth orifice is provided in the middle of a fourth passage for guiding refrigerant gas downstream of the pressure control valve and upstream of the pressure reducing means to the discharge control valve, and the third orifice is provided. It is preferable that the cross-sectional area of the passage of the wheel is smaller than the cross-sectional area of the passage of the fourth orifice.
  • the flow rate of the refrigerant gas in the fourth passage is reduced by the fourth orifice, and the refrigerant gas in the discharge chamber flows into the discharge control valve. Since the shock applied to the discharge control valve at that time is reduced, the damage received by the discharge control valve is reduced, and the durability and reliability are improved.
  • a part of the first passage is constituted by a hole formed in an annular body fixed to the rotating shaft.
  • the swash plate comes into contact with the annular body when the inclination angle of the swash plate is minimized, but the annular body rotates integrally with the swash plate, so that the swash plate is fixed to the housing or the housing.
  • the swash plate wear is suppressed as compared with the case where a structure that makes contact with the annular body is adopted.
  • the third passage includes a front-side bearing accommodating space for accommodating a shaft seal and a front-side bearing on the front side of the rotating shaft, and the crank chamber.
  • each bearing and the shaft seal are lubricated and cooled by the lubricating oil in the refrigerant gas passing through the third passage, and seizure occurs. Can be prevented.
  • FIG. 1 is a vertical sectional view showing a state in which a discharge passage of a variable displacement type swash plate type clutchless compressor according to an embodiment of the present invention is open.
  • FIG. 2 is a partially enlarged view showing a state where the discharge passage is opened.
  • FIG. 3 is a longitudinal sectional view showing a state in which a discharge passage of a variable displacement type swash plate type clutchless compressor according to an embodiment of the present invention is closed.
  • FIG. 4 is a partially enlarged view showing a state where the discharge passage is closed.
  • FIG. 5 is a longitudinal sectional view showing a state in which a discharge passage of a variable displacement type swash plate type clutchless compressor according to another embodiment of the present invention is closed.
  • FIG. 6 is a partially enlarged view of a rear head of the variable displacement type swash plate type clutchless compressor shown in FIG. 5, showing a state in which a discharge passage is closed.
  • FIG. 7 is a partially enlarged view of a rear head of the variable displacement type swash plate type clutchless compressor of FIG. 5, showing a state in which a discharge passage is opened.
  • FIG. 8 is an enlarged cross-sectional view showing different cross-sections of a rear head of the variable-capacity swash plate type clutchless compressor of FIG. 5, and is a view showing a fourth passage.
  • FIG. 1 is a longitudinal sectional view showing a state in which a discharge passage of a variable displacement type swash plate type clutchless compressor according to an embodiment of the present invention is open
  • FIG. 2 is a partially enlarged view thereof
  • FIG. I is a longitudinal sectional view showing a closed state
  • FIG. 4 is a partially enlarged view of FIG.
  • One end of the cylinder block 1 of this variable capacity swash plate type clutchless compressor has a lid head 3 via a valve plate 2 and the other end has a front head 4 Are fixed respectively.
  • the cylinder block 1 has a plurality of cylinder bores 6 at predetermined intervals in the circumferential direction around a shaft (rotation axis) 5. It is arranged.
  • a piston 7 is slidably accommodated in each of the cylinder pores 6.
  • a crank chamber 8 is formed in the front head 4, and a swash plate 10 is accommodated in the crank chamber 8.
  • the sliding surface 10a of the swash plate 10 holds the spherical end 11a of the connecting groove 11a on the sliding surface 10a.
  • the retainer 53 is mounted on the boss 10b of the swash plate 10 via a radial bearing 55, and the retainer 53 is rotatable relative to the swash plate 10.
  • the radial bearing 55 is prevented from coming off by a flange 54 fixed to the boss 10b with a screw 45.
  • the other end 1 lb of the connecting groove 11 is fixed to the piston 7.
  • the shroud 50 is composed of a housing body 51 that supports the tip end surface of the connecting groove 11a so as to be relatively rotatable, and the one end 11a of the connecting groove 11a. It consists of a washer 52 that supports the rear end face so that it can roll relatively.
  • a discharge chamber 12 and a suction chamber 13 are formed in the lid 3.
  • the suction chamber 13 is arranged so as to surround the discharge chamber 12.
  • Riahead 3 is provided with an inlet (not shown) that leads to the outlet of the evaporator (not shown).
  • FIG. 2 is an enlarged longitudinal sectional view showing a state where the discharge passage 39 is open
  • FIG. 4 is an enlarged longitudinal sectional view showing a state where the discharge passage 39 is closed.
  • a check valve (discharge control valve) 31 is provided in the middle of the discharge passage 39 that connects the discharge chamber 12 and the discharge port 1a.
  • the discharge passage 39 has a passage 39 a formed in the lid 3 and a discharge passage 39 a. And a passage 39b formed in the lube plate 2.
  • the passage 39 b leads to a discharge port 1 a formed in the cylinder block 1.
  • a spring (biasing member) 32 is housed in the bottomed cylindrical check valve 31, and a stopper 56 fixed to the lid 3 with a cap 59 is provided in a stopper 56.
  • One end of the spring 32 is in contact, and the other end of the spring 32 is in contact with the bottom of the check valve 31.
  • the internal space 33 of the check valve 31 communicates with the crank chamber 8 via a passage 34.
  • the urging force of the spring 32 and the pressure of the crank chamber 8 act in the valve closing direction (the direction in which the valve opening decreases).
  • the check valve 31 When the check valve 31 is opened, the discharge port la and the discharge chamber 12 communicate with each other through the discharge passage 39 (see FIG. 2). Therefore, on the other side (lower side) of the check valve 31, the pressure of the discharge port 1 a and the pressure of the discharge chamber 12 act in the valve opening direction (the direction in which the valve opening increases).
  • the check valve 31 moves in the closing direction, the discharge passage 39 is shut off, and the check valve 3 is closed.
  • a control valve (pressure control valve) 81 is provided in the middle of the passage 57.
  • the valve body 81b is seated by energizing the solenoid (not shown) of the control port 81, and the second passage 57 is shut off.
  • the valve body 81b is closed by stopping power supply to the solenoid.
  • the second passageway 57 is opened away from it.
  • the operation of the control valve 81 is controlled by a computer (not shown).
  • the suction chamber 13 and the crank chamber 8 communicate with each other via a first passage 58.
  • the first passage 58 has an orifice (second orifice) 58 a formed in the valve plate 2 and a passage 58 b formed in the cylinder opening 1. And a hole 58 c formed in a ring (annular body) 59 fixed to the shaft 5.
  • the suction chamber 13 and the crank chamber 8 communicate with each other via a third passage 60.
  • the third passage 60 includes a passage 60 a formed in the front head 4, a front bearing housing space 60 b formed in the front head 4, A passage 60 c formed in the shaft 5, a rear-side bearing accommodating space 60 d formed in the cylinder block 1, a passage 58 b of the cylinder block 1, and a valve plate 2 orifice 58a.
  • the passage 58b of the cylinder block 1 and the orifice 58a of the valve plate 2 form a part of the first passage 58 and the passage 58b of the third passage 60.
  • An internal thread 61 is formed on the inner peripheral surface of the rear end of the passage 60c, and a screw -62 is screwed into the internal thread 61.
  • An orifice (first orifice) 62 a is formed in the screw 62, and the passage area of the orifice 62 a forms a part of the first passage 58. Smaller than the passage area of the orifice 58a of the valve plate 2. Therefore, the third passage is provided only when the boss portion 10b of the swash plate 10 almost blocks the hole 58c of the ring 59 and the passage cross-sectional area of the first passage 58 is greatly reduced. The refrigerant gas in the crank chamber 8 is led to the suction chamber 13 through 60. W
  • the valve plate 2 has a discharge port 16 for communicating the compression chamber 82 with the discharge chamber 12 and a suction port 15 for communicating the compression chamber with the suction chamber 13 in the circumferential direction. Are provided at predetermined intervals.
  • the discharge port 16 is opened and closed by a discharge valve 17, and the discharge valve 17 is connected to a bolt 19 and a nut 20 together with a valve retainer 18 on the rear end face of the valve plate 2. More fixed.
  • the suction port 15 is opened and closed by a suction valve 21, and the suction valve 21 is disposed between the valve plate 2 and the cylinder block 1.
  • Shaft 5 is provided by radial bearings (Rear bearings) 24 and thrust bearings (Lear bearings) 25 housed in the rear bearing housing space 60 d of cylinder block 1.
  • the radial end (front side bearing) of the front head 4 is rotatably supported, and the radial bearing (front side bearing) 26 accommodated in the front side bearing housing space 60 b of the front head 4.
  • the front end of the shaft 5 is rotatably supported.
  • a shaft seal 46 is housed in the bearing housing space 60 b on the front side.
  • a female screw 1 b is provided at the center of the cylinder block 1, and an Asian nut 83 is screwed to the female screw 1 b.
  • a preload is applied to the shaft 5 via the thrust bearing 25.
  • a pulley (not shown) is fixed to the front end of the shaft 5.
  • a thrust flange 40 for transmitting the rotation of the shaft 5 to the swash plate 10 is fixed to the shaft 5, and the thrust flange 40 is a thrust bearing 33.
  • the thrust flange 40 and the swash plate 10 are connected via a hinge mechanism 41, and the swash plate 10 can be inclined with respect to an imaginary plane perpendicular to the shaft 5.
  • the swash plate 10 is slidably and tiltably mounted on the shaft 5.
  • the hinge mechanism 41 includes a bracket 1 Oe provided on the front surface 10 c of the swash plate 10 and a linear guide groove 10 provided on the bracket 10 e. f, and a rod 43 screwed to the swash plate side end face 40a of the thrust flange 40.
  • the longitudinal axis of the guide groove 10 f is inclined by a predetermined angle with respect to the front surface 10 c of the swash plate 10.
  • the spherical portion 43a of the rod 43 is fitted into the guide groove 10f so as to be relatively slidable.
  • variable capacity type swash plate type clutchless compressor Next, the operation of the variable capacity type swash plate type clutchless compressor will be described.
  • the rotational power of the vehicle-mounted engine is constantly transmitted to a pulley (not shown) and a shaft 5 via a belt (not shown), and the rotating power of the shaft 5 is a thrust flange 40 and a hinge mechanism 41. Is transmitted to the swash plate 10 through the rotation of the swash plate 10.
  • the rotation of the swash plate 10 causes the shower 50 to relatively rotate on the rear surface 10a of the swash plate 10, so that the rotation force from the swash plate 10 causes the linear reciprocating motion of the piston 7 Is converted to
  • the piston 7 reciprocates in the cylinder bore 6, and as a result, the volume of the compression chamber 82 in the cylinder bore 6 changes.
  • This change in volume causes the suction, compression and discharge of the refrigerant gas to be performed sequentially.
  • the refrigerant gas having a capacity corresponding to the inclination angle of the swash plate 10 is discharged.
  • the suction valve 21 opens, and low-pressure refrigerant flows from the suction chamber 13 to the compression chamber 82 in the cylinder bore 6.
  • the discharge valve 17 is opened, and high-pressure refrigerant gas is discharged from the compression chamber 82 to the discharge chamber 12.
  • the refrigerant gas in the crank chamber 8 flows from the passage 60 a of the front head 4 to the front-side bearing housing space 60 b, the passage 60 c of the shaft 5, The air flows into the suction chamber 13 through the bearing housing space 60 d, the passage 58 b of the cylinder block 1, and the orifice 60 f of the valve plate 2.
  • the refrigerant gas is throttled by the orifice 62 a of the screw 62 in the middle of the passage 60 c of the shaft 5, and then is re-cooled by the orifice 58 a of the knob plate 2. And the pressure decreases.
  • the pressure of the crank chamber 8 is applied to one of the check valves 31 as a discharge control valve, and the pressure of the discharge chamber 12 is applied to the other of the check valves 31.
  • a relatively small spring force is used as the spring 32 that urges the check valve 31 in the valve closing direction, so that the heat load is reduced and discharge is performed.
  • variable-capacity swash plate type clutchless compressor of this embodiment has the following effects.
  • the suction chamber 13 Since there is no need to install a mechanism that opens and closes the suction port in the shaft 5 (conventional transmission cylinder, blocking body, etc.), the suction chamber 13 is located outside the discharge chamber 12 inside the rear head 3. They can be placed, making it easier to manage seals with the outside air. Furthermore, since the spring for giving the pre-opening to the shaft 5 does not cut off as the shaft 5 rotates and the inlet 3a cannot be opened and closed, the reliability of the compressor is improved. improves.
  • the adjust nut 8 3 can be tightened to provide a sufficient pre-opening to the shaft 5, so that the shaft 5 and the thrust flange 40 are stabilized in the axial direction and the vibration Control noise I can do it.
  • check valve 31 is employed as the discharge control valve, the configuration can be simplified.
  • the pressure difference between the crank chamber 8 and the discharge chamber 12 is smaller than the pressure difference between the suction chamber 13 and the discharge chamber 12 and the pressure in the crank chamber 8 is Focusing on the fact that the pressure does not change significantly due to load fluctuations compared to the pressure of the valve, the pressure of the crank chamber 8 acts on one of the spool valves 31 as a discharge control valve, and the other of the check valves 31 Since the structure for applying the pressure of the discharge chamber 12 was adopted, a relatively small spring force could be used as the spring 32 for biasing the check valve 31 in the valve closing direction. As a result, when the pressure in the discharge chamber 12 gradually decreases as the heat load decreases, the check valve 31 is kept open until the minimum piston stroke (extremely low load) is achieved. Can be kept.
  • a variable displacement swash plate type clutchless compressor having a structure in which the pressure of the suction chamber acts on one of the check valves as the discharge control valve and the pressure of the discharge chamber acts on the other of the check valves. Since the pressure difference between the suction chamber and the discharge chamber is large in A spring with a relatively large spring force must be used as a spring that biases in the valve closing direction. In addition, the pressure in the suction chamber changes greatly due to load fluctuations. As a result, when the pressure in the discharge chamber gradually decreases as the heat load decreases, the check valve operates before the minimum piston stroke occurs, the discharge passage is shut off, and refrigerant gas is released. It may not flow out from the discharge port to the capacitor side. According to this embodiment, such a problem is solved.
  • the fourth passage 60 Since a part of the fourth passage 60 is constituted by the front-side bearing housing space 60 and the rear-side bearing housing space 60d, the lubricating oil of the refrigerant gas passing through the third passage 60 is used.
  • the bearings 26, 24, 25 and the shaft seal 46 are lubricated and cooled.
  • the check valve 31 is used as the discharge control valve.
  • a valve other than the check valve such as the spool valve or the one-way valve may be used. Good.
  • FIG. 5 is a longitudinal sectional view showing a state in which a discharge passage of a variable capacity type swash plate type clutchless compressor according to another embodiment of the present invention is closed
  • FIG. 6 is a variable capacity type shown in FIG.
  • FIG. 7 is a partially enlarged view of a swash plate type clutchless compressor, showing a state in which a discharge passage is closed.
  • FIG. 7 is a rear head of the variable displacement type swash plate type clutchless compressor shown in FIG.
  • Fig. 8 is an enlarged cross-sectional view showing a different cross section of the rear head of the variable capacity swash plate type clutchless compressor shown in Fig. 5;
  • FIG. 14 is a diagram showing a fourth passage.
  • the refrigerant gas in the crank chamber 8 is guided to one of the check valves 31 as a pressure control valve, and the pressure control valve is closed. Then, as described later, Refrigerant gas in the discharge chamber 112 was directly introduced to one of the check valves 133 as a control valve, and the pressure control valve was closed.
  • a check valve 13 1 is provided in the middle of the discharge passage 13 9 that connects the discharge chamber 1 12 and the discharge port la.
  • the discharge passage 139 is constituted by a passage 139 a formed in the head 103 and a passage 39 formed in the knob plate 2.
  • the passage 139 b leads to a discharge port 1 a formed in the cylinder block 1.
  • a spring (biasing member) 13 2 is housed in the bottomed check valve 13 1, and one end of the spring 13 2 abuts the annular holder 56, and the other end of the spring 3 2
  • Check valve 31 is in contact with the bottom surface.
  • a cap 15 9 is fixed to the lid 10 3, and the annular holder 56 is pressed against the cap 15 9 by the biasing force of the spring 13 2.
  • the internal space 133 of the check valve 13 1 communicates with the crank chamber 8 via the passage 13 4.
  • One side (upper side) of the check valve 13 1 has the urging force of the spring (biasing member) 13 2 and the pressure of the refrigerant gas guided through the fourth passage 71 1 in the valve closing direction (valve opening direction). In the direction of decreasing degree).
  • the discharge port 1 a communicates with the discharge chamber 1 12 via the discharge passage 1 39. Therefore, on the other side (lower side) of the check valve 131, the pressure of the discharge port la and the pressure of the discharge chamber 112 act in the valve opening direction (the direction in which the valve opening increases).
  • the pressure difference between one of the check valves 13 1 and the other is When the pressure falls below the predetermined value, the check valve 13 1 moves in the valve closing direction to block the discharge passage 13 9, and the discharge chamber 1 12 is located below the check valve 13 1. Only pressure acts in the valve opening direction. In other words, the pressure of the discharge port 1 a does not work below the check valve 13 1.
  • a control valve (pressure control valve) 81 is provided in the middle of passage 157.
  • An orifice (third orifice) 70 is provided on the second passageway 15 7 and downstream of the control valve 81 as pressure reducing means. The pressure of the refrigerant gas guided from the discharge chamber 112 to the crank chamber 8 is reduced by the heat 70.
  • the valve body 81 is seated by energizing the solenoid (not shown) of the control valve 81, and the second passage 157 is shut off.
  • the valve body 8 lb is separated from the valve seat and the second passage 157 is opened by stopping the power supply to the solenoid.
  • the operation of the control valve 81 is controlled by a computer (not shown).
  • the section 157a on the second passageway 157 and between the downstream of the control valve 81 and the upstream of the orifice 70 and the interior of the check valve 131 The space 13 3 communicates with the space 13 via a fourth passage 71 formed in the head 103.
  • an orifice (fourth orifice) 72 is mounted in the middle of the fourth passage 71.
  • the flow rate of the refrigerant gas guided from the fourth passage 71 to the internal space 13 3 of the check valve 13 1 is reduced by the orifice 72.
  • the passage cross-sectional area of the first orifice 70 is smaller than the passage cross-sectional area of the orifice 72.
  • the first passage 158 includes a passage 158 a formed in the valve plate 2, a passage 58 b formed in the cylinder block 1, and a ring fixed to the shaft 5. And a hole 58c formed in 59.
  • This embodiment differs from the embodiment shown in FIG. 1 in that the passage 158a formed in the valve plate 2 is not an orifice.
  • the third passage 60 includes a passage 60 a formed in the front head 4, a front bearing housing space 60 b formed in the front head 4, The passage 60 c formed in the foot 5, the rear bearing housing space 60 d formed in the cylinder block 1, the passage 58 b of the cylinder block 1, and the valve plate 2 It is composed of 158 a.
  • the passage 58b of the cylinder block 1 and the passage 158a of the valve plate 2 constitute a part of the first passage 58 and a part of the third passage 60. Make up the part.
  • Sent to The discharge acting on the lower side of the check valve 13 1 is the sum of the pressure acting on the upper side of the check valve 13 1 (the pressure in the internal space 13 3) and the biasing force of the spring 13 2.
  • the check valve 13 1 moves in the valve closing direction and the discharge passage 13 9 is shut off (see FIG. 6).
  • the outflow of the refrigerant gas from the discharge port 1a to the capacitor 84 is prevented.
  • the boss portion 10b of the swash plate 10 almost closes the hole 58c of the ring 59 and the passage cross-sectional area of the first passage 58 is greatly reduced.
  • the refrigerant gas in the crank chamber 8 flows into the suction chamber 13 through the passage 60. This suppresses an excessive rise in the pressure of the crank chamber 8 and allows the refrigerant gas to circulate in the compressor.
  • the refrigerant gas enters the suction chamber 113, the compression chamber 82, the discharge chamber 112, the second passage 157, and the crank chamber 8. And the third passage 60 sequentially returns to the suction chamber 113 again.
  • variable-capacity swash plate type clutchless compressor according to this embodiment has the same effects as the above-described embodiment, and also has the following effects.
  • the check valve 13 1 was driven by directly introducing the refrigerant gas from the discharge chamber 1 12 into one of the check valves 13 1 (internal space 13 3). 13 1 responsiveness is improved. As a result, the amount of refrigerant discharged (the capacity of the compressor) can be changed quickly, and cooling filling is improved.
  • the check valve 13 1 operates reliably even under operating conditions such as high load and high rotation, for example, when the pressure in the crank chamber 8 cannot increase quickly as the pressure in the discharge chamber 112 increases. Since the refrigerating capacity can be reduced to zero, in order to ensure the operation of the check valve 131, the passage cross-sectional area of the first communication passage 58 is reduced and the crank chamber is reduced. There is no need to set the pressure of 8 higher. Therefore, damage to parts such as the retainer 53 pulling the piston 7 in the crank chamber 8 and the shaft seal 46 that shuts off the crank chamber 8 from the atmosphere is not affected. It becomes smaller, and the durability and reliability of the compressor are improved.
  • one passage 71 is provided as the fourth passage, but a plurality of passages may be provided.
  • one orifice (orifice 70) is installed as a depressurizing means, a plurality of orifices may be installed or an orifice may be used as another depressurizing means. Instead of mounting the face 70, the passage cross-sectional area in the middle of the second passage 157 may be reduced.
  • the check valve 13 1 is used as the discharge control valve.
  • a spool valve or a port valve (not shown) or the like is used instead of the check valve 13 1, a spool valve or a port valve (not shown) or the like is used. May be used. Industrial applicability
  • variable-capacity swash plate type clutchless compressor according to the present invention is suitable as a refrigerant compressor of a vehicle air conditioner.

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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)

Abstract

L'invention concerne un compresseur sans embrayage du type à plateau oscillant à déplacement variable, dans lequel lorsque la charge thermique passe en dessous d'un seuil, un passage (58) est ouvert par une vanne de commande (81) de façon à amener la pression du carter de vilebrequin (8) à monter et l'inclinaison d'un plateau oscillant (10) à descendre. La zone en coupe d'un second passage (57) est remarquablement réduite par le plateau oscillant (10), de façon à minimiser la diminution de pression dans le carter de vilebrequin (8) lorsque l'inclinaison dudit plateau oscillant (10) devient minimale. Un chemin de distribution (39a) est fermé par un clapet de retenue (31) lorsque la pression du carter de vilebrequin (8) monte, cette pression étant appliquée sur un côté du clapet de retenue (31), alors que la pression de la chambre de refoulement (12) est appliquée à l'autre côté dudit clapet de retenue, du fait que la différence de pression entre le carter de vilebrequin (8) et la chambre de refoulement (12) est plus petite et plus stable que celle entre la chambre d'alimentation (13) et la chambre de refoulement (12). De ce fait, lorsque la pression de la chambre de refoulement diminue graduellement lorsque la charge thermique passe en-dessous d'un seuil, la course du piston est réduite au minimum et le clapet de retenue peut être maintenu ouvert jusqu'à ce que le plateau oscillant (10) réduise la zone de passage du premier passage.
PCT/JP1999/003203 1998-06-16 1999-06-16 Compresseur sans embrayage du type a plateau oscillant a deplacement variable WO1999066203A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP99925334A EP1088991A1 (fr) 1998-06-16 1999-06-16 Compresseur sans embrayage du type a plateau oscillant a deplacement variable

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP18558298 1998-06-16
JP10/185582 1998-06-16

Publications (1)

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WO1999066203A1 true WO1999066203A1 (fr) 1999-12-23

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1365150A1 (fr) * 2001-01-29 2003-11-26 Zexel Valeo Climate Control Corporation Compresseur sans embrayage a came plate a cylindree variable
US7014428B2 (en) 2002-12-23 2006-03-21 Visteon Global Technologies, Inc. Controls for variable displacement compressor
WO2011005367A3 (fr) * 2009-07-06 2011-03-10 Carrier Corporation Soupape de décompression de dérivation pour régulation de la capacité d'un compresseur

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005018673A1 (de) * 2005-04-21 2006-10-26 Behr Gmbh & Co. Kg Klimaanlage, insbesondere für ein Kraftfahrzeug

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07127566A (ja) * 1993-11-05 1995-05-16 Toyota Autom Loom Works Ltd クラッチレス片側ピストン式可変容量圧縮機

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07127566A (ja) * 1993-11-05 1995-05-16 Toyota Autom Loom Works Ltd クラッチレス片側ピストン式可変容量圧縮機

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1365150A1 (fr) * 2001-01-29 2003-11-26 Zexel Valeo Climate Control Corporation Compresseur sans embrayage a came plate a cylindree variable
EP1365150A4 (fr) * 2001-01-29 2006-06-07 Zexel Valeo Climate Contr Corp Compresseur sans embrayage a came plate a cylindree variable
US7014428B2 (en) 2002-12-23 2006-03-21 Visteon Global Technologies, Inc. Controls for variable displacement compressor
WO2011005367A3 (fr) * 2009-07-06 2011-03-10 Carrier Corporation Soupape de décompression de dérivation pour régulation de la capacité d'un compresseur
US10337507B2 (en) 2009-07-06 2019-07-02 Carrier Corporation Bypass unloader valve for compressor capacity control

Also Published As

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