EP1092873A2 - Alésages dans le cylindre d'un compresseur à plateau en biais - Google Patents

Alésages dans le cylindre d'un compresseur à plateau en biais Download PDF

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Publication number
EP1092873A2
EP1092873A2 EP20000119831 EP00119831A EP1092873A2 EP 1092873 A2 EP1092873 A2 EP 1092873A2 EP 20000119831 EP20000119831 EP 20000119831 EP 00119831 A EP00119831 A EP 00119831A EP 1092873 A2 EP1092873 A2 EP 1092873A2
Authority
EP
European Patent Office
Prior art keywords
piston
cylinder bore
drive shaft
compressor
groove
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Withdrawn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
EP20000119831
Other languages
German (de)
English (en)
Inventor
Manabu K.K. Toyoda Jidoshokki Seisakusho Sugiura
Kazuaki K.K. Toyoda Jidoshokki Seisakusho Iwama
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
Toyoda Jidoshokki Seisakusho KK
Toyoda Automatic Loom Works Ltd
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 Toyoda Jidoshokki Seisakusho KK, Toyoda Automatic Loom Works Ltd filed Critical Toyoda Jidoshokki Seisakusho KK
Publication of EP1092873A2 publication Critical patent/EP1092873A2/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Withdrawn legal-status Critical Current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
    • 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
    • F04B27/1045—Cylinders
    • 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
    • F04B2027/184—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
    • F04B2027/1886—Open (not controlling) fluid passage
    • F04B2027/1895—Open (not controlling) fluid passage between crankcase and suction chamber

Definitions

  • the present invention relates to a piston type compressor which compresses refrigerant gas such as a compressor in an air-conditioner for vehicles.
  • a piston 102 reciprocates according to a back-and-forth oscillating movement of a swash plate 101 (right and left in Fig. 10).
  • Refrigerant gas is sucked into a compression chamber 104 defined in a cylinder bore 103. Then, the gas is compressed, and the compressed refrigerant gas is discharged from the compression chamber 104.
  • a main body 105 of the piston 102 which is inserted into a cylinder bore 103, is hollow.
  • an inertia force acting on each part of a compressor due to the reciprocating movement is diminished.
  • a stress acting on a coupling portion 106 between the piston 102 and the swash plate 101 is reduced, which results in an increased durability of the piston 102.
  • a crank chamber 108 In a housing 107 of the compressor, a crank chamber 108, in which the swash plate 101 is accommodated, has numerous sliding portions such as a coupling portion through shoes 109 between the piston 102 and a swash plate 101. It is necessary to supply a sufficient amount of lubricating oil to the crank chamber 108 to lubricate these sliding portions. Blow-by gas (leakage of the refrigerant gas) from the compression chamber 104 functions as one of the lubricating means. The lubricating oil with the blow-by gas is supplied from the compression chamber 104 to the crank chamber 108.
  • a high dimensional accuracy in clearance is needed between an outer circumferential surface 105a of the main body 105 of the piston 102 and an inner circumferential surface 103a of the cylinder bore 103 to adjust the amount of the blow-by gas supplied from the compression chamber 104 into the crank chamber 108.
  • a groove 105b is formed in the outer circumferential surface 105a of the main body of the piston 105, and that a blow-by gas passage 110 which connects the compression chamber 104 with the crank chamber 108 is defined between this groove 105b and the inner circumferential surface 103a of the cylinder bore 103.
  • the main body 105 of the piston 102 is produced by the following process so that it can be produced easily.
  • a cylinder having an equal thickness is formed (a cylinder having an equal thickness contributes to an improvement of an accuracy of finishing, for example since a metal mold can be made simply for a forging or a casting of the main body 105) and then the groove 105b for this cylinder is drilled.
  • the thickness of the portion in which the groove 105b is formed becomes thinner than that of the other portions.
  • the portion in which this groove 105b is formed has the thickness necessary to keep a certain strength, the other portions which occupy the most portion of the main body 105 has a greater thickness than is necessary.
  • the weight of the piston 102 cannot be effectively reduced by hollowing the main body 105, either.
  • the invention is achieved by recognizing the problem existing in the conventional art.
  • the object is to offer a compressor in which the weight of the piston can be effectively reduced by hollowing a main body, even when a blow-by gas passage is provided.
  • the compressor according to the present invention has a following mechanism.
  • a crank chamber is formed and a drive shaft is rotatably supported to extend in the crank chamber in the housing.
  • a cam plate is integrally rotatably coupled on the drive shaft in the crank chamber.
  • a cylinder bore is formed in a cylinder block which constitutes a part of the housing.
  • a piston connected to the cam plate is inserted and arranged so that a compression chamber is defined in the cylinder bore.
  • This piston comprises a hollow main body inserted into the cylinder bore and a connecting portion connecting the main body to the cam plate.
  • the invention has a feature that a groove for a gas, which serves as a communicating means, is formed in the inner circumferential surface of the cylinder bore and a blow-by gas passage is defined between the groove and the outer circumferential surface of the main body of the piston to communicate the compression chamber with the crank chamber.
  • the main body of the piston for example, can be a simple cylinder with an equal thickness. Accordingly, the problem that the portion in the main body of the piston corresponding to the blow-by gas passage becomes thinner than the other portions, is avoided. This means that the other portions occupying most of the main body of the piston do not need to be thicker than is necessary.
  • the blow-by gas passage is provided as well, the weight of the piston can be effectively reduced by utilizing a hollow main body.
  • the present invention has a feature that the groove for a gas is a straight line extending in the direction of the axis of the cylinder bore.
  • the groove (the blow-by gas passage) is simply a straight line and it can be formed in the inner circumferential surface of the cylinder bore more easily and more accurately than the following spiral groove, for example.
  • the groove has a spiral shape around the axis of the cylinder bore.
  • the groove has a spiral shape, so it extends to cross the direction of the reciprocating movement of the piston. Accordingly, it is highly expected that for example, a foreign substance involved between the outer circumferential surface of the main body and the inner circumferential surface of the cylinder bore is taken into the groove by the reciprocating movement of the piston, and that the foreign substance got into this groove with the blow-by gas flowing the blow-by gas passage is discharged into the crank chamber.
  • a plurality of the grooves are formed in the inner circumferential surface of the cylinder bore.
  • a plurality of blow-by gas passages are provided, even if one of the blow-by gas passages is blocked up by the foreign substance, the blow-by gas to the crank chamber or supply of a lubricating oil can be maintained by the other blow-by gas passages.
  • the present invention has a feature that the cam plate is inclinably connected with the drive shaft and the inclination angle of the cam plate is changed by adjusting the pressure in the crank chamber so that the discharge capacity of the compressor can be changed.
  • the piston has to slide smoothly in the cylinder bore and follow the cam plate which changes the inclination angle by adjusting the pressure in the crank chamber. Accordingly, when the weight of the piston is effectively reduced and the inertia force acting on the cam plate is diminished, this inertia force diminishes the influence on the control of the inclination angle of the cam plate and the control of the displacement is improved.
  • the compressor is of a fixed capacity type, and the inclination angle of the cam plate is fixed.
  • the capacity of such a fixed capacity compressor is not influenced in accordance with the rotating speed of the drive shaft. It is always operated at the same inclination angle, that is, the maximum inclination angle of the variable capacity displacement compressor. Accordingly, when the drive shaft rotates at high speed, the speed of the reciprocating movement of the piston is increased excessively in a state continuously maintaining a long stroke of the piston. So, the inertia force acting on various parts of the fixed capacity compressor, due to the reciprocating movement of this piston with heavy weight, at long stroke, at high speed, may be excessive. In a fixed capacity type compressor, which may be in such a severe condition (that is, at high speed and long stroke), if the piston reduces its weight, the inertia force can be diminished effectively.
  • the piston has a piston ring around the outer circumferential surface of its main body.
  • Such an arrangement with a piston ring is inferior to the arrangement that the outer circumferential surface of the main body directly contacts the inner circumferential surface of the cylinder bore, with respect to the proper leakage of the blow-by gas from the compression chamber to the crank chamber.
  • the exclusive blow-by gas passage is particularly effective.
  • the piston ring on the piston side does not need machining (such as a notching or a through hole) for the blow-by gas passage and it can save the machining time.
  • a first embodiment to a fifth embodiment of a compressor used for a vehicle air conditioner according to the present invention will now be described. Besides, a second embodiment to a fifth embodiment are explained only about the differences from a first embodiment, so the same numbers are used for the same kind of members and the explanation is omitted.
  • a front housing 11 is secured to the front side of a cylinder block 12.
  • a rear housing 13 is secured through a valve plate assembly 14 to the back of the cylinder block 12.
  • the front housing 11, the cylinder block 12 and the rear housing 13 constitute a housing assembly in a compressor.
  • a crank chamber 15 is defined by the front housing 11 and the cylinder block 12.
  • a drive shaft 16 is rotatably supported by the front housing 11 and the cylinder block 12 so that it is extended through the crank chamber 15.
  • the drive shaft 16 is connected with a vehicle engine as an external drive source which is not illustrated, through a clutch mechanism such as a magnetic clutch which is not illustrated. Accordingly, the drive shaft 16 is rotated and driven by the connection of the clutch mechanism when the vehicle engine is operated.
  • a rotor 19 is mounted on the drive shaft 16 in the crank chamber 15.
  • a swash plate 20, such as a cam plate, is supported slidably and inclinably in the direction of the axis L on the drive shaft 16.
  • a hinge mechanism 21 is located between the rotor 19 and the swash plate 20.
  • the swash plate 20 is inclinable and rotatable integrally with the drive shaft 16 by the hinge mechanism 21.
  • the inclination angle of the swash plate 20 decreases, and when the swash plate 20 moves to the rotor 19 side, the inclination angle of the swash plate 20 increases.
  • a plurality of (only one cylinder bore is illustrated in the drawings) cylinder bores 18 are formed in the cylinder block 12, around the axis L of the drive shaft 16, parallel to this axis L.
  • One side of a single-headed piston 22 is accommodated in the cylinder bore 18 and the other side of it is engaged with the outer periphery of the swash plate 20 through a shoe 23.
  • a compression chamber 17 is defined in the cylinder bore 18 between the front surface of the piston 22 and the valve plate assembly 14. As the swash plate 20 rotates, it wobbles back and forth in the direction of the axis L, and that causes the piston 22 to reciprocate back and forth in the cylinder bore 18. As a result, the volume in the compression chamber 17 changes.
  • a suction chamber 24 and a discharge chamber 25 are respectively defined in the rear housing 13.
  • a plurality of suction ports 26, suction valves 27, discharge ports 28 and discharge valves 29 are respectively formed on the valve plate assembly 14.
  • Refrigerant gas in the suction chamber 24 is sucked into the compression chamber 17 through the suction port 26 and the suction valve 27 while the piston 22 moves from the top dead center to the bottom dead center.
  • the refrigerant gas which is drawn into the compression chamber 17 is compressed to a certain pressure as the piston 22 moves from the bottom dead center to the top dead center. Then the compressed gas is discharged to the discharge chamber 25 through the discharge port 28 and the discharge valve 29.
  • a bleeding passage 30 communicates between the crank chamber 15 and the suction chamber 24.
  • the bleeding passage 30 comprises a passage 30a which is formed along the axis of the drive shaft 16, and a through hole 30b which is formed in the cylinder block 12 and the valve plate assembly 14.
  • a supply passage 31 communicates between the discharge chamber 25 and the crank chamber 15.
  • a displacement control valve 32 such as a magnetic valve, is placed in the supply passage 31.
  • the displacement control valve 32 comprises a solenoid 32a and a valve body 32b which opens and closes the supply passage 31 when the solenoid 32a is excited and de-excited.
  • the solenoid 32a of the displacement control valve 32 is excited and de-excited under the control of the computer, which is not illustrated, with reference to a cooling load. Accordingly, the degree of opening of the supply passage 31 is adjusted by the valve body 32b and the pressure in the crank chamber 15 is increased in response to the opening of the supply passage 31. So the difference between the pressure in the crank chamber 15 and the pressure in the compression chamber 17, which acts on the front and rear sides of the piston 22, is adjusted. As a result, the inclination angle of the swash plate 20 is changed and the amount of the stroke of the piston 22 is changed, and thereby adjusts the discharge capacity. When the amount of the stroke of the piston 22 is changed, the position of the bottom dead center of the piston 22 is changed, but the position of the top dead center of it (illustrated in Fig. 1) is unchanged.
  • the valve body 32b opens the supply passage 31 and the discharge chamber 25 and the crank chamber 15 are communicated. Accordingly, the high pressure refrigerant gas in the discharge chamber 25 is supplied to the crank chamber 15 through the supply passage 31 and the pressure in the crank chamber 15 rises.
  • the pressure in the crank chamber 15 rises the inclination angle of the swash plate 20 decreases. And so the amount of the stroke of the piston 22 is decreased and the discharge capacity is minimized.
  • valve body 32b closes the supply passage 31, and the pressure in the crank chamber 15 is lowered due to the pressure release through the bleeding passage 30.
  • the pressure in the crank chamber 15 is lowered, the inclination angle of the swash plate 20 increases. So the amount of the stroke of the piston 22 is increased and the discharge capacity is maximized.
  • the piston 22 is constituted of a main body 35, which is hollow and accommodated in the cylinder bore 18, and of a connecting portion 36, which connects the main body 35 with the swash plate 20. These two portions are connected in the direction of the axis S of the cylinder bore 18.
  • the connecting portion 36 includes a concave portion 36a in the inner circumferential surface (in the side of the axis L of the drive shaft 16) and in this concave portion 36a a pair of shoe seats 36b, which is concave spherical shape, is formed face to face in the direction of the axis S.
  • a pair of shoes 23 are accommodated in the concave portion 36a, respectively slidably supported by the corresponding shoe seats 36b.
  • the swash plate 20 is held between the front and rear shoes 23 at the outer periphery of the swash plate 20.
  • the main body 35 is constituted by a cylindrical portion 37, which has a bottom surface on the side of the compression chamber 17 (on the side of the valve plate assembly 14) in the cylinder bore 18, and by a cover portion 38, which closes the inner space of the cylindrical portion 37 and is formed separately from the cylindrical portion 37.
  • the cover portion 38 is integrally formed with the connecting portion 36.
  • the cylindrical portion 37 and the cover portion 38 (or the connecting portion 36) are separately made by means such as casting or forging with metallic material of Aluminum alloys. And then they are joined such as welding or frictional welding.
  • a wear resistance film C may be applied to the outer circumferential surface 35a of the main body 35.
  • the main material of the wear resistance film C is a solid lubricant such as PTFE (polytetrafulloloethylene) and is coated on the outer circumferential surface 35a, for example, from 20 to 40 ⁇ m in thickness.
  • the object of the wear resistance film C is to decrease the sliding friction between the outer circumferential surface 35a of the main body 35 and the inner circumferential surface 18a of the cylinder bore 18, and then to prevent both the circumferential surfaces 35a and 18a from deteriorating due to the friction caused by the reciprocating movement of the piston 22.
  • a groove 18b is formed in the inner circumferential surface 18a of the cylinder bore 18.
  • the blow-by gas passage 39 which communicates the compression chamber 17 with the crank chamber 15 is constituted between the groove 18b and the outer circumferential surface 35a of the main part 35.
  • the groove 18b is a straight line and extends parallel to the axis S, from an opening portion to the crank chamber 15 toward the valve plate assembly 14 in the inner circumferential surface 18a of the cylinder bore 18.
  • the length of the groove 18b is determined so that the groove 18b is closed against the compression chamber 17 by the outer circumferential surface 35a of the main body 35 when the piston 22 is at the top dead center (illustrated in Figs. 1 and 4). That is, the blow-by gas passage 39 is constituted so that the communication between the compression chamber 17 and the crank chamber 15 is disconnected when the piston 22 is at the top dead center.
  • the end portion of the groove 18b on the side of the valve plate assembly 14 is constituted so that the connecting portion 18c between the groove 18b and the inner circumferential surface 18a of the cylinder bore 18 does not have a sharp edge.
  • the groove 18b is formed so that the bottom surface of it is gradually sloped to the outer circumferential surface 35a of the main body 35 on the side of the valve plate assembly 14. Accordingly, in particular, when the piston 22 moves from the bottom dead center to the top dead center in the process of the compression and discharge, the connecting portion between the bottom surface of the groove 18b and the inner circumferential surface 18a of the cylinder bore 18 is prevented from hitting the piston 22 (the outer circumferential surface 35a of the main body) and so the damage of the piston 22 is prevented.
  • the imaginary straight line D extends intersecting the axis L of the drive shaft 16 and the axis S of the cylinder bore 18.
  • the position of the intersecting point P1 located at the farther side with respect to the axis L of the drive shaft 16 is hereby referred to as the twelve o'clock position.
  • the position of the intersecting point P2, located at the nearer side with respect to the axis L is hereby referred to as the six o'clock position.
  • the groove 18b is formed in the inner circumferential surface 18a of the cylinder bore 18 corresponding to the quarter range which extends between nine o'clock and twelve o'clock, in detail, at the ten o'clock position on the outer circumferetial surface 35a of the main body 35.
  • the blow-by of the refrigerant gas from the compression chamber 17 to the crank chamber 15 proceeds mainly through the exclusive blow-by gas passage 39 and lubricating oil suspended in the refrigerant gas in the compression chamber 17 is supplied to the crank chamber 15 with the blow-by gas.
  • the lubricating oil is supplied to the crank chamber 15 to lubricate each sliding portion such as the portion between the piston 22 (the shoe seat 36b) and the shoe 23, and the portion between the shoe 23 and the swash plate 20.
  • the lubricating oil is supplied initially in the refrigerating circuit in the vehicle air conditioner, and conveyed to the compression chamber with the refrigerant gas.
  • the embodiment of the above arrangement has the following effects.
  • FIG. 6 A second embodiment is illustrated in Fig. 6.
  • the groove 18b (the blow-by gas passage 39) is formed in a spiral around the axis S of the cylinder bore 18 with one or more than one wind (with two wind in this embodiment).
  • the length of the groove 18b extending to the valve plate assembly 14 is determined so that the groove 18b is not closed by the outer circumferential surface 35a of the main body 35 even when the piston 22 is at the top dead center. That is, the blow-by gas passage 39 always communicates between the compression chamber 17 and the crank chamber 15, regardless of the position of the stroke of the piston 22.
  • This embodiment also has an effect such as "1" and "4" of the first embodiment.
  • the groove 18b is formed in a spiral, it extends in the direction crossing with the direction of the reciprocating movement of the piston 22. Accordingly, for example it is highly expected that foreign substances disposed between the outer circumferential surface 35a of the main body and the inner circumferential surface 18a of the cylinder bore 18 are taken into the groove 18b by the reciprocating movement of the piston 22, and the foreign substances are discharged into the crank chamber 15 with the blow-by gas flowing in the blow-by gas passage 39. Thus the foreign substances disposed between the circumferential surfaces 35a and 18a are effectively discharged, and so, for example, peeling off the wear resistance film C caused by the foreign substances can be prevented.
  • the lubricating oil conveyed in the blow-by gas passage 39 in a spiral (the circumferential direction of the outer circumferential surface 35a) satisfactorily lubricates whole the circumference between both the circumferential surfaces 35a and 18a.
  • a third embodiment is illustrated in Fig. 7.
  • a plurality (two) of the spiral grooves 18b are formed.
  • Two grooves 18b are formed so that each groove winds in the opposite direction to the other one. Therefore, the grooves cross each other at a plurality of points.
  • This embodiment also has not only an effect such as "1" and "4" of the first embodiment, but also has the following effect.
  • FIG. 8 A fourth embodiment is illustrated in Fig. 8.
  • the swash plate 20 is integrally and rotatably fixed on the drive shaft 16 to rotate integrally and the inclination angle is fixed (in this embodiment, the inclination angle is the same as the maximum inclination angle of the swash plate 20 of the variable displacement compressor because of the relation to the following explanation). That is, the compressor in this embodiment is a fixed displacement compressor.
  • the fixed displacement compressor is always operated at the same condition (that the swash plate 20 is inclined at the maximum angle) as the state of the maximum discharge capacity of the variable displacement compressor, regardless of the speed of rotation of the drive shaft 16 since the inclination angle of the swash plate 20 is fixed. Accordingly, when the drive shaft 16 rotates at a high speed, the speed of the reciprocating movement of the piston 22 is increased excessively and there is the possibility that the inertia force acting on various parts of the compressor caused by the reciprocating movement of the piston 22 is excessive. It is particularly worthwhile that the weight of the piston 22 in a compressor which has to meet such severe conditions, is effectively reduced.
  • a fifth embodiment is illustrated in Fig. 9.
  • the piston 22 in this embodiment has a piston ring 41 around the outer circumferential surface 35a of the main body 35 and is contacted on the inner circumferential surface 18a of the cylinder bore 18 through the piston ring 41.
  • the piston ring 41 satisfactorily adheres to the inner circumferential surface 18a of the cylinder bore 18 due to its flexibility. Consequently, it is an ideal arrangement from the point of view of providing a firm seal between the outer circumferential surface 35a of the main body 35 and the inner circumferential surface 18a of the cylinder bore 18.
  • the arrangement including the piston ring 41 is inferior to the arrangement of the other embodiment (the arrangement that both the circumferential surfaces 35a and 18a directly contact) as for setting the clearance or the blow-by gas passage to leak the blow-by gas properly from the compression chamber 17 to the crank chamber 15. Accordingly, when the exclusive blow-by gas passage 39 is provided in such an arrangement, it is particularly worthwhile in a point of view that it can accurately set the amount of the blow-by gas, for example.
  • the weight of the piston can be effectively reduced by hollowing the main body, even if the blow-by gas passage is provided. Accordingly, the inertia force acting on the various parts of the compressor caused by the reciprocating movement of the piston can be decreased. For example, a stress acting on a connecting portion between the piston and the cam plate is decreased and so the piston can be accomplished durability.
  • a compressor is constituted so that the refrigerant gas is compressed in a compression chamber, as the rotating movement of a drive shaft is converted to the reciprocating movement of a piston through a cam plate.
  • the object is to offer a compressor in which the weight of the piston can be effectively reduced by hollowing a main body thereof, even when a blow-by gas passage is provided.
  • a groove is formed in the inner circumferential surface of a cylinder bore.
  • the blow-by gas passage which communicates the compression chamber with a crank chamber, is constituted between the groove and the outer circumferential surface of the main body of the piston.

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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)
EP20000119831 1999-10-13 2000-09-12 Alésages dans le cylindre d'un compresseur à plateau en biais Withdrawn EP1092873A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP29116999A JP2001107847A (ja) 1999-10-13 1999-10-13 圧縮機
JP29116999 1999-10-13

Publications (1)

Publication Number Publication Date
EP1092873A2 true EP1092873A2 (fr) 2001-04-18

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EP20000119831 Withdrawn EP1092873A2 (fr) 1999-10-13 2000-09-12 Alésages dans le cylindre d'un compresseur à plateau en biais

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JP (1) JP2001107847A (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1394411A2 (fr) * 2002-08-30 2004-03-03 Kabushiki Kaisha Toyota Jidoshokki Compresseur à déplacement variable du type à disque oblique
CN107013491A (zh) * 2017-05-24 2017-08-04 安徽寅时压缩机制造有限公司 一种具有内置翻转过滤机构的压缩机

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1394411A2 (fr) * 2002-08-30 2004-03-03 Kabushiki Kaisha Toyota Jidoshokki Compresseur à déplacement variable du type à disque oblique
EP1394411A3 (fr) * 2002-08-30 2004-07-07 Kabushiki Kaisha Toyota Jidoshokki Compresseur à déplacement variable du type à disque oblique
US7186096B2 (en) 2002-08-30 2007-03-06 Kabushiki Kaisha Toyota Jidoshokki Swash plate type variable displacement compressor
CN107013491A (zh) * 2017-05-24 2017-08-04 安徽寅时压缩机制造有限公司 一种具有内置翻转过滤机构的压缩机

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