EP2886864B1 - Kondensator - Google Patents

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Publication number
EP2886864B1
EP2886864B1 EP13823006.5A EP13823006A EP2886864B1 EP 2886864 B1 EP2886864 B1 EP 2886864B1 EP 13823006 A EP13823006 A EP 13823006A EP 2886864 B1 EP2886864 B1 EP 2886864B1
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EP
European Patent Office
Prior art keywords
discharge port
valve body
discharge
compressor
outlet end
Prior art date
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Active
Application number
EP13823006.5A
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English (en)
French (fr)
Other versions
EP2886864A4 (de
EP2886864A1 (de
Inventor
Kazutaka Hori
Takashi Shimizu
Konichi TANAKA
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.)
Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/1073—Adaptations or arrangements of distribution members the members being reed valves
    • F04B39/1086—Adaptations or arrangements of distribution members the members being reed valves flat annular reed valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/1073—Adaptations or arrangements of distribution members the members being reed valves
    • F04B39/108—Adaptations or arrangements of distribution members the members being reed valves circular reed valves
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/1085—Valves; Arrangement of valves having means for limiting the opening height
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F04C29/126—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type
    • F04C29/128—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type of the elastic type, e.g. reed valves
    • 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
    • F04B2201/00—Pump parameters
    • F04B2201/06—Valve parameters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/32—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
    • F04C18/322—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and reciprocating with respect to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2250/00—Geometry
    • F04C2250/10—Geometry of the inlet or outlet
    • F04C2250/102—Geometry of the inlet or outlet of the outlet
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/7879—Resilient material valve
    • Y10T137/7888—With valve member flexing about securement
    • Y10T137/7891—Flap or reed

Definitions

  • the present invention relates to compressors having a discharge valve.
  • Patent Document 1 discloses a rotary compressor which has a so-called reed valve as a discharge valve.
  • Patent Document 2 also discloses a discharge valve similar to the discharge valve in Patent Document 1.
  • the discharge valve is provided at a main bearing.
  • the discharge valve has a plate-like valve body provided so as to cover an outlet end of a discharge port.
  • the valve body closes the discharge port and prevents a back-flow of a fluid into the compression chamber.
  • the valve body is elastically deformed and is separated from the outlet end of the discharge port.
  • the high-pressure fluid in the compression chamber passes through the outlet end of the discharge port and the valve body, and flows out.
  • EP 2 441 960 A1 discloses a refrigerant compressor and heat pump device. By way of both reducing an amplitude of pressure pulsations and reducing pressure losses in a discharge muffler space into which is discharged a refrigerant compressed at a compression unit, compressor efficiency is enhanced.
  • a low-stage discharged muffler space is formed in the shape of a ring around a drive shaft. In the low-stage discharge muffler space, a discharge port rear guide is provided in the proximity of a discharge port through which is discharged the refrigerant compressed by a low-stage compression unit.
  • the discharged port rear guide is provided at a flow path in one direction out of two flow paths from the discharge port to a communication port in different directions around the drive shaft, and prevents the refrigerant from flowing in that direction, thereby causing the refrigerant to circulate in a forward direction in the ring-shape discharge muffler space.
  • EP 1 160 447 A2 relates to a piston compressor discharge port.
  • the discharge port comprises a tapered first diameter-increasing portion and a tapered second diameter-increasing portion.
  • the cross-sectional areas of the first diameter-increasing portion and the second diameter-increasing portion increase from the upstream toward the downstream of the discharge port.
  • the rate of increase of the cross-sectional area of the second diameter-increasing portion is designed so as to be greater than that of the first diameter-increasing portion.
  • the second diameter-increasing portion is connected to the first diameter-increasing portion and the maximum cross-sectional area of the first diameter-increasing portion is equal to the minimum cross-sectional area of the second diameter-increasing portion.
  • EP 0 926 345 A2 relates to a shape of suction hole and discharge hole of refrigerant compressor.
  • Discharge holes and suction holes having shapes that suppress the turbulence of a refrigerant gas flow is disclosed.
  • the shape of the discharge hole has a tapered surface wall, such that the circumference of the discharge hole increases from the piston cylinder surface to the discharge chamber surface.
  • the shape of the suction hole has a tapered surface wall such that the circumference of the suction hole increases from the suction chamber surface to the piston cylinder surface. It allows the flow path of the refrigerant gas to flow approximately tangential to the valve reed by providing a tapered surface wall. The flow resistance of the discharge hole or the suction hole is reduced such that the volume efficiency of the compressor is improved and compressor noise is suppressed.
  • JP 2011 043084 A discloses a rotary compressor.
  • Said rotary compressor includes an upper end plate for defining an operating chamber in which an intake refrigerant can be compressed, and a discharge valve for opening and closing a discharge hole which is formed in a lower end plate.
  • the discharge hole includes a communicating portion, a valve seat portion formed in an edge portion of the communicating portion, and an enlarged width portion formed to continue into the communicating portion so as to enlarge the width toward a discharge direction of the compressed refrigerant.
  • An inner circumferential side generatrix which is extended to a top portion from an inside bottom portion of the valve seat portion is formed to be a sloped straight line.
  • An outer circumferential side generatrix line which is extended to an outer bottom portion from the top portion of the valve sitting portion is formed to be a circular arc.
  • the inventors of the present application found that once the lift amount of the valve body of the discharge valve exceeds a predetermined degree, the pressure loss at the time when a fluid flows out from the discharge port is not much reduced even if the lift amount is further increased. The reason why this happens is as follows. As will be explained in detail later, the greater the lift amount of the valve body of the discharge valve is, the larger a vortex formed around the outlet end of the discharge port becomes. The vortex interrupts a flow of the fluid passing through the gap between the outlet end of the discharge port and the valve body.
  • the pressure loss at the time when a fluid flows out from the discharge port is not much reduced even if the lift amount of the valve body is further increased, because of an increase in the effects of the vortex.
  • the present invention is thus intended to improve the efficiency of a compressor by appropriately setting a lift amount of a valve body of a discharge valve.
  • the first aspect of the present invention is directed to a compressor having a fixed side member (45) which forms a compression chamber (36) and a movable side member (38) which is rotated and changes a volume of the compression chamber (36), the compressor configured to suck a fluid into the compression chamber (36) and compress the fluid.
  • the fixed side member (45) is provided with a discharge port (50) that penetrates the fixed side member (45) and leads the fluid out of the compression chamber (36), and a discharge valve (60) that opens/closes the discharge port (50),
  • a discharge port (50) is formed in the fixed side member (45) of the compressor (10).
  • the inlet end (51) of the discharge port (50) communicates with the compression chamber (36).
  • the outlet end (52) of the discharge port (50) is opened/closed by the valve body (61) of the discharge valve (60). In the state in which the valve body (61) of the discharge valve (60) covers the outlet end (52) of the discharge port (50), a back-flow of a fluid from outside the fixed side member (45) into the discharge port (50) is prevented by the valve body (61).
  • the peripheral length Li of the inlet end (51) of the discharge port (50) is a wetted perimeter length of the inlet end (51) of the discharge port (50).
  • the distance between the outlet end (52) of the discharge port (50) and the valve body (61) (that is, a lift amount of the valve body (61)) is uniform around the entire outlet end (52) of the discharge port (50).
  • the cross sectional area Ao of the outlet side flow path (70) formed between the outlet end (52) of the discharge port (50) and the valve body (61) is equal to a surface area (i.e., Lo ⁇ h) of a cylinder having a peripheral length equal to the peripheral length Lo of the outlet end (52) of the discharge port (50), and a height equal to the lift amount h of the valve body (61).
  • the discharge valve (60) is a reed valve
  • the valve body (61) is tilted with respect to the outlet end (52) of the discharge port (50), and therefore the distance between the outlet end (52) of the discharge port (50) and the valve body (61) is not uniform around the outlet end (52) of the discharge port (50).
  • the wetted perimeter length of the outlet side flow path (70) formed between the outlet end (52) of the discharge port (50) and the valve body (61) is twice the peripheral length Lo of the outlet end (52) of the discharge port (50).
  • the wetted perimeter length of the outlet side flow path (70) can be approximately 2Lo.
  • a ratio (Do/Di) of the hydraulic diameter Do of the outlet side flow path (70) to the hydraulic diameter Di of the inlet end (51) of the discharge port (50) is 0.5 or less (Do/Di ⁇ 0.5).
  • the hydraulic diameter Do of the outlet side flow path (70) is twice the reference lift amount ho.
  • the reference lift amount ho of the valve body (61) of the discharge valve (60) is set to a value according to the hydraulic diameter Di of the inlet end (51) of the discharge port (50).
  • the second aspect of the present invention is that in the first aspect of the present invention, the ratio (Do/Di) of the hydraulic diameter Do of the outlet side flow path (70) to the hydraulic diameter Di of the inlet end (51) of the discharge port (50) is 0.4 or less.
  • the ratio (Do/Di) of the hydraulic diameter Do of the outlet side flow path (70) to the hydraulic diameter Di of the inlet end (51) of the discharge port (50) is 0.4 or less (Do/Di ⁇ 0.4).
  • the reference lift amount ho of the valve body (61) of the discharge valve (60) is set to a value according to the hydraulic diameter Di of the inlet end (51) of the discharge port (50).
  • the third aspect of the present invention is that in the first or second aspect of the present invention, the ratio (Do/Di) of the hydraulic diameter Do of the outlet side flow path (70) to the hydraulic diameter Di of the inlet end (51) of the discharge port (50) is 0.25 or more.
  • the fourth aspect of the present invention is that in any one of the first to third aspects of the present invention, the fixed side member (45) is provided with a chamfered portion (56) along the entire periphery of the outlet end (52) of the discharge port (50).
  • the chamfered portion (56) of the fixed side member (45) is provided along the entire periphery of the outlet end (52) of the discharge port (50).
  • the cross sectional area of the flow path of the discharge port (50) closer to the outlet end (52) is gradually increased toward the outlet end (52) of the discharge port (50).
  • the area of the outlet end (52) of the discharge port (50) is larger than in the case where the chamfered portion (56) is not provided.
  • the area of the outlet end (52) of the discharge port (50) is equal to an area (i.e., a pressure receiving area) of the valve body (61) covering the outlet end (52) of the discharge port (50) to which pressure is applied from the discharge port (50).
  • a pressure receiving area of the valve body (61) covering the outlet end (52) of the discharge port (50) to which pressure is applied from the discharge port (50).
  • the fifth aspect of the present invention is that in the fourth aspect of the present invention, a height H of the chamfered portion (56) in an axial direction of the discharge port (50) and a width W of the chamfered portion (56) in a direction orthogonal to the axial direction of the discharge port (50) satisfy a relationship of 0 ⁇ H/W ⁇ 0.5.
  • the volume of the discharge port (50) is a dead volume which is not changed even if the movable side member (38) rotates. Thus, to improve the efficiency of the compressor (10), a smaller volume of the discharge port (50) is preferable.
  • the chamfered portion (56) formed on the fixed side member (45) has such a shape of which the height H and the width W satisfy the relationship 0 ⁇ H/W ⁇ 0.5. That is, the height H of the chamfered portion (56) is less than half the width W of the chamfered portion (56).
  • the sixth aspect of the present invention is that in any one of the first to fifth aspects of the present invention, a cross sectional shape of the discharge port (50) is an oblong or an ellipse.
  • a discharge port (50) whose cross sectional shape is an oblong or an ellipse is formed in the fixed side member (45).
  • the reference lift amount ho of the valve body (61) of the discharge valve (60) is set such that the ratio (Do/Di) of the hydraulic diameter Do of the outlet side flow path (70) to the hydraulic diameter Di of the inlet end (51) of the discharge port (50) is 0.5 or less.
  • the lift amount of the valve body (61) is set to such a value, the reference lift amount ho of the valve body (61) becomes a relatively small value, and a vortex generated at the time when a fluid passes between the outlet end (52) of the discharge port (50) and the valve body (61) is downsized.
  • the pressure loss of the fluid at the time when the fluid flows out from the discharge port (50) can be reduced, and the efficiency of the compressor (10) can be improved.
  • the discharge valve (60) If the discharge valve (60) is not closed at an appropriate timing, the fluid discharged from the compression chamber (36) through the discharge port (50) may flow back to the discharge port (50). On the other hand, if the lift amount of the valve body (61) of the discharge valve (60) is increased, it takes longer time for the valve body (61) to travel, and the timing at which the valve body (61) closes the outlet end (52) of the discharge port (50) may be delayed from the appropriate timing. If the valve body (61) delays in closing the outlet end (52) of the discharge port (50), the amount of fluid flowing back to the compression chamber (36) from outside the fixed side member (45) is increased and the efficiency of the compressor (10) is reduced.
  • the timing at which the valve body (61) closes the outlet end (52) of the discharge port (50) is determined such that the reference lift amount ho of the valve body (61) is relatively small.
  • the delay of timing at which the valve body (61) closes the outlet end (52) of the discharge port (50) can be reduced, and the amount of fluid flowing back to the compression chamber (36) from outside the fixed side member (45) can be reduced.
  • the efficiency of the compressor (10) can be improved in the present invention.
  • the reference lift amount ho of the valve body (61) of the discharge valve (60) is determined such that the ratio (Do/Di) of the hydraulic diameter Do of the outlet side flow path (70) to the hydraulic diameter Di of the inlet end (51) of the discharge port (50) is 0.4 or less.
  • the delay in timing at which the valve body (61) closes the outlet end (52) of the discharge port (50) can be further reduced.
  • the amount of fluid flowing back to the compression chamber (36) from outside the fixed side member (45) can be further reduced, and as a result, the efficiency of the compressor (10) can be further improved.
  • the outlet end (52) of the discharge port (50) is closed by the valve body (61) of the discharge valve (60) at an appropriate timing.
  • the lift amount of the valve body (61) of the discharge valve (60) is equal to or smaller than a certain degree, further reduction in the lift amount of the valve body (61) does not contribute to an efficiency improvement of the compressor (10).
  • the reference lift amount ho of the valve body (61) of the discharge valve (60) is determined such that the ratio (Do/Di) of the "hydraulic diameter Do of the outlet side flow path (70)" to the "hydraulic diameter Di of the inlet end (51) of the discharge port (50)" is 0.25 or more and 0.5 or less (0.25 ⁇ Da/Di ⁇ 0.5) or 0.25 or more and 0.4 or less (0.25 ⁇ Do/Di ⁇ 0.4).
  • the reference lift amount ho of the valve body (61) can be set in a range where the amount of fluid flowing back to the compression chamber (36) can be reduced.
  • the chamfered portion (56) around the entire periphery of the outlet end (52) of the discharge port (50) is formed on the fixed side member (45).
  • the area of the outlet end (52) of the discharge port (50) is increased, compared to the case in which the chamfered portion (56) is not formed on the fixed side member (45).
  • the chamfered portion (56) of the fifth aspect of the present invention has such a shape of which the height H and the width W satisfy the relationship 0 ⁇ H/W ⁇ 0.5. Thus, it is possible to reduce an amount of increase in volume of the discharge port (50), while maintaining the pressure receiving area of the valve body (61) covering the outlet end (52) of the discharge port (50).
  • a compressor (10) of the present embodiment is provided in a refrigerant circuit which performs a vapor compression refrigeration cycle, and the compressor (10) suctions a refrigerant evaporated in an evaporator and compresses the refrigerant.
  • the compressor (10) of the present embodiment is a hermetic compressor which accommodates, in a casing (11), a compressor mechanism (30) and an electric motor (20).
  • the casing (11) is a cylindrical closed container, standing upright.
  • the casing (11) has a cylindrical barrel (12) and a pair of end plates (13, 14) which close the both ends of the barrel (12).
  • a suction pipe (15) is attached to a lower portion of the barrel (12).
  • a discharge pipe (16) is attached to the upper end plate (13).
  • the electric motor (20) is positioned above the compressor mechanism (30).
  • the electric motor (20) has a stator (21) and a rotor (22).
  • the stator (21) is fixed to the barrel (12) of the casing (11).
  • the rotor (22) is attached to a drive shaft (23) of the compressor mechanism (30), described later.
  • the compressor mechanism (30) is positioned at a lower portion in the casing (11).
  • the compressor mechanism (30) is a so-called oscillating piston type rotary fluid machine.
  • the compressor mechanism (30) has a front head (31), a cylinder (32), and a rear head (33).
  • the cylinder (32) is a disk-shaped thick member (see FIG. 2 ).
  • the front head (31) is a plate-like member which closes the upper end surface of the cylinder (32).
  • a main bearing (31a) which supports the drive shaft (23) is arranged to project from a central portion of the front head (31).
  • the rear head (33) is a plate-like member which closes the lower end surface of the cylinder (32).
  • An auxiliary bearing (33a) which supports the drive shaft (23) is arranged to project from a central portion of the rear head (33).
  • the cylinder (32) is fixed to the barrel (12) of the casing (11).
  • the front head (31), the cylinder (32), and the rear head (33) are fastened together with bolts, and form a fixed side member (45).
  • the compressor mechanism (30) has a drive shaft (23).
  • the drive shaft (23) has a main shaft (24) and an eccentric portion (25).
  • the eccentric portion (25) is positioned at a lower portion of the main shaft (24).
  • the eccentric portion (25) is in a columnar shape with a diameter larger than the diameter of the main shaft (24), and is eccentric with respect to the main shaft (24).
  • an oil supply path is formed in the drive shaft (23).
  • the lubricating oil accumulated in the bottom of the casing (11) is supplied to sliding portions of the bearings (31a, 33a) and the compressor mechanism (30) through the oil supply path.
  • the compressor mechanism (30) has a piston (38) as a movable side member and a blade (43).
  • the piston (38) is in a slightly thick cylindrical shape.
  • the eccentric portion (25) of the drive shaft (23) is rotatably fitted in the piston (38).
  • An outer circumferential surface (39) of the piston (38) slides on an inner circumferential surface (35) of the cylinder (32).
  • the compression chamber (36) is formed between the outer circumferential surface (39) of the piston (38) and the inner circumferential surface (35) of the cylinder (32).
  • the blade (43) is a flat plate-like member projecting from the outer circumferential surface (39) of the piston (38), and is integrally formed with the piston (38).
  • the blade (43) separates the compression chamber (36) into a high-pressure chamber (36a) and a low-pressure chamber (36b).
  • the compressor mechanism (30) has a pair of bushes (41).
  • the pair of bushes (41) are fitted in a bush groove (40) of the cylinder (32), and sandwich the blade (43) from both sides.
  • the blade (43) integrally formed with the piston (38) is supported on the cylinder (32) via the bushes (41).
  • the cylinder (32) is provided with a suction port (42) that penetrates the cylinder (32) in the radius direction.
  • the suction port (42) communicates with the low-pressure chamber (36b) of the compression chamber (36).
  • One end of the suction port (42) is open on the inner circumferential surface (35) of the cylinder (32).
  • the open end of the suction port (42) which is open on the inner circumferential surface (35) is located near the bushes (41) (on the right side of the bushes (41) in FIG. 2 ).
  • the suction pipe (15) is inserted in the other end of the suction port (42).
  • a discharge port (50) is formed in the front head (31).
  • the discharge port (50) is a through hole which penetrates the front head (31) in the thickness direction of the front head (31) (see FIG. 1 ).
  • the discharge port (50) communicates with the high-pressure chamber (36a) of the compression chamber (36).
  • the open end of the discharge port (50) which is open on the lower surface of the front head (31) is located opposite to the suction port (42) with respect to the bushes (41) (on the left side of the bushes (41) in FIG. 2 ).
  • the shape of the discharge port (50) will be described in detail later.
  • the front head (31) is provided with a discharge valve (60), which is a reed valve. As shown in FIG. 3 , the discharge valve (60) is attached to the upper surface of the front head (31).
  • the discharge valve (60) has a valve body (61), a valve guard (62), and a securing pin (63).
  • the valve body (61) is an elongated, thin flat plate-like member.
  • a material for the valve body (61) is spring steel, for example.
  • the valve body (61) is provided such that its end portion covers an outlet end (52) of the discharge port (50).
  • a front surface (61a) of the valve body (61) is brought into tight contact with a periphery (52a) of the outlet end (52) of the discharge port (50).
  • the valve guard (62) is a slightly thick metallic member with a high stiffness.
  • the valve guard (62) is in an elongated plate-like shape corresponding to the shape of the valve body (61). Further, an end portion of the valve guard (62) is slightly curved upward.
  • the valve guard (62) is arranged to overlap the valve body (61).
  • the proximal portion of the valve guard (62) and the proximal portion of the valve body (61) are fixed to the front head (31) with the securing pin (63).
  • the discharge port (50) is closed in the state in which the valve body (61) covers the outlet end (52) of the discharge port (50).
  • the discharge port (50) is open in the state in which the valve body (61) is lifted from the outlet end (52) of the discharge port (50).
  • the compressor mechanism (30) of the present embodiment is a rotary fluid machine which has the cylinder (32), the front head (31) and the rear head (33) which serve as closing members for closing end portions of the cylinder (32), the piston (38) which is accommodated in the cylinder (32) and eccentrically rotates, and the blade (43) which separates the compression chamber (36) formed between the cylinder (32) and the piston (38) into a low-pressure side and a high-pressure side.
  • gas pressure (pressure in the dome) in the internal space of the casing (11) is applied to a back surface (61b) of the valve body (61) of the discharge valve (60).
  • the discharge valve (60) is in the closed state as shown in FIG. 3A .
  • the piston (38) moves, and the gas pressure in the high-pressure chamber (36a) gradually increases and exceeds the pressure in the dome, the end portion of the valve body (61) of the discharge valve (60) separates from the outlet end (52) of the discharge port (50). As a result, the discharge valve (60) is open as shown in FIG. 3B .
  • the gas refrigerant in the high-pressure chamber (36a) passes through the discharge port (50) and flows between the outlet end (52) of the discharge port (50) and the valve body (61), and is discharged to the internal space of the casing (11) (that is, outside the compressor mechanism (30)).
  • the high-pressure gas refrigerant discharged from the compressor mechanism (30) passes through the discharge pipe (16) and is led outside the casing (11).
  • discharge port (50) The shape of the discharge port (50) will be described in detail with reference to FIG. 5 and FIG. 6 .
  • the discharge port (50) is a straight through hole which penetrates the front head (31) in the plate thickness direction (see FIG. 5 ).
  • An inlet end (51) of the discharge port (50) is open on the front surface (i.e., the surface facing the cylinder (32)) of the front head (31).
  • the outlet end (52) of the discharge port (50) is open on the back surface (i.e., the surface opposite to the surface facing the cylinder (32)) of the front head (31).
  • a portion around the outlet end (52) of the discharge port (50) is raised from its surrounding area, and serves as a seat portion (55).
  • the cross section of the flow path of the discharge port (50) (i.e., the cross section orthogonal to the axial direction of the discharge port (50)) is in an oblong shape (see FIG. 6 ).
  • the discharge port (50) is arranged such that its shorter diameter is along the radius dimension of the inner circumferential surface (35) of the cylinder (32) (see FIG. 2 ).
  • the front head (31) is provided with a chamfered portion (56) along the periphery (52a) of the outlet end (52) of the discharge port (50).
  • the chamfered portion (56) is formed around the entire periphery of the outlet end (52) of the discharge port (50) (see FIG. 6 ).
  • the chamfered portion (56) is formed such that the height H in the axial direction of the discharge port (50) and the width W in a direction orthogonal to the axial direction of the discharge port (50) are respectively uniform around the entire periphery of the chamfered portion (56) (see FIG. 5 ).
  • the height H and the width W of the chamfered portion (56) satisfy the following formula: 0 ⁇ H/W ⁇ 0.5. That is, the height H of the chamfered portion (56) is less than half of the width W of the chamfered portion (56) (0 ⁇ H ⁇ W/2).
  • a portion of the discharge port (50) at a position lower than the chamfered portion (56) forms a main pass (53).
  • the cross section of the flow path of the main pass (53) is in an oblong shape having an arc portion with a curvature radius Ri and a straight portion with a length Ls. Further, the shape of the cross section of the flow path of the main pass (53) is uniform along the entire length thereof. That is, the longer diameter length D 1 and the shorter diameter length D 2 of the cross section of the flow path of the main pass (53) are respectively uniform along the entire length of the main pass (53). Accordingly, the shape of the inlet end (51) of the discharge port (50) is also in an oblong shape having an arc portion with the curvature radius Ri and a straight portion with the length Ls.
  • an area of the outlet end (52) of the discharge port (50) is larger than in the case in which the front head (31) is not provided with the chamfered portion (56).
  • the area of the outlet end (52) of the discharge port (50) is equal to an area (i.e., a pressure receiving area) of a portion of the front surface (61a) of the valve body (61) to which pressure is applied from the discharge port (50).
  • the area of the outlet end (52) of the discharge port (50) is increased, it means that the pressure receiving area of the valve body (61) is increased, and the force in a direction separating the valve body (61) from the outlet end (52) of the discharge port (50) is increased.
  • the volume of the discharge port (50) is a dead volume which is not changed even if the piston (38) rotates.
  • the height H of the chamfered portion (56) is set to less than half of the width W of the chamfered portion (56), considering an efficiency improvement caused by a reduction of the loss by overcompression, and an efficiency decrease caused by an increase of the dead volume.
  • a lift amount of the valve body (61) of the discharge valve (60) is determined such that pressure loss of the gas refrigerant at the time when the gas refrigerant is discharged from the compressor mechanism (30) can be reduced to low level, and such that a reduction in efficiency of the compressor (10) due to delay in closing the valve body (61) of the discharge valve (60) can be reduced.
  • a reference lift amount ho of the valve body (61) of the discharge valve (60) is determined, based on a hydraulic diameter Di of the inlet end (51) of the discharge port (50).
  • the inlet end (51) of the discharge port (50) is in an oblong shape having the arc portion with the curvature radius Ri and the straight portion with the length Ls.
  • the length (i.e., the peripheral length Li) of the periphery (51a) of the inlet end (51) of the discharge port (50) is expressed by Equation 1 shown below, and the area Ai thereof is expressed by Equation 2 shown below.
  • the peripheral length Li of the inlet end (51) of the discharge port (50) is a wetted perimeter length of the inlet end (51) of the discharge port (50).
  • the inlet end (51) of the discharge port (50) of the present embodiment has the arc portion with the curvature radius Ri of 2.1 mm, and the straight portion with the length Ls of 5.3 mm.
  • the peripheral length Li is 23.8 mm; the area Ai is 36.1 mm 2 ; and the hydraulic diameter Di is 6.1 mm.
  • the reference lift amount ho of the valve body (61) of the discharge valve (60) is the maximum lift amount of the valve body (61) on a center line CL of the discharge port (50). That is, the reference lift amount ho is a distance from the "outlet end (52) of the discharge port (50)" to the "front surface (61a) of the valve body (61)” on the center line CL of the discharge port (50) in the state in which the entire back surface (61b) of the valve body (61) touches the valve guard (62).
  • the center line CL of the discharge port (50) is a straight line passing an intersection point of the longer diameter and the shorter diameter of the inlet end (51) of the discharge port (50) and an intersection point of the longer diameter and the shorter diameter of the outlet end (52) of the discharge port (50).
  • the center line CL is orthogonal to the inlet end (51) and the outlet end (52) of the discharge port (50).
  • the front surface (61a) of the valve body (61) is tilted with respect to the outlet end (52) of the discharge port (50) in the state in which the entire back surface (61b) of the valve body (61) touches the valve guard (62).
  • the distance (that is, the lift amount of the valve body (61)) from the outlet end (52) of the discharge port (50) to the front surface (61a) of the valve body (61) has a maximum value of h 1 , and a minimum value of h 2 .
  • the outlet end (52) of the discharge port (50) is in an oblong shape. Further, as shown in FIG. 5 , in the state in which the valve body (61) is lifted from the outlet end (52) of the discharge port (50), the front surface (61a) of the valve body (61) is tilted with respect to the outlet end (52) of the discharge port (50).
  • the outlet side flow path (70) has a cross-sectional shape as shown in FIG. 7A (that is, the same shape as a side surface of a tubular object having a top surface tilted with respect to its bottom surface).
  • a lower periphery (72) of the outlet side flow path (70) is in the same oblong shape as the periphery (52a) of the outlet end (52) of the discharge port (50).
  • an upper periphery (71) of the outlet side flow path (70) is in the shape obtained by projecting the periphery (52a) of the outlet end (52) of the discharge port (50) to the front surface (61a) of the valve body (61).
  • the height of the outlet side flow path (70) has a maximum value of h 1 , and a minimum value of h 2 .
  • the front surface (61a) of the valve body (61) is not curved and is substantially flat in the state in which the entire back surface (61b) of the valve body (61) touches the valve guard (62).
  • the reference lift amount ho of the valve body (61) is substantially equal to an average value ((h 1 + h 2 ) / 2) of the maximum value h 1 and the minimum value h 2 of the lift amount of the valve body (61). Therefore, a cross sectional area of the actual outlet side flow path (70) shown in FIG. 7A is substantially equal to the cross sectional area of a virtual outlet side flow path (75) shown in FIG. 7B .
  • the front surface (61a) of the valve body (61) is parallel to the outlet end (52) of the discharge port (50), and in the case where the distance from the outlet end (52) of the discharge port (50) to the front surface (61a) of the valve body (61) is the reference lift amount ho, the virtual outlet side flow path (75) is a flow path formed between the outlet end (52) of the discharge port (50) and the valve body (61).
  • the cross sectional shape of the virtual outlet side flow path (75) is the same as a side surface of a tubular object having a top surface parallel to its bottom surface.
  • the virtual outlet side flow path (75) shown in FIG. 7B is treated as being substantially equivalent to the actual outlet side flow path (70) shown in FIG. 7A .
  • the hydraulic diameter of the actual outlet side flow path (70) shown in FIG. 7A is treated as being substantially equal to the hydraulic diameter of the virtual outlet side flow path (75) shown in FIG. 7B , and is calculated based on the following Equations 4-6.
  • the shape of the outlet end (52) of the discharge port (50) is an oblong shape having an arc portion with a curvature radius Ro and a straight portion with a length Ls.
  • Each of an upper periphery (76) and a lower periphery (77) of the virtual outlet side flow path (75) is in the same shape as the outlet end (52) of the discharge port (50), similarly to the lower periphery (72) of the actual outlet side flow path (70).
  • the peripheral length of the virtual outlet side flow path (75) is equal to the peripheral length Lo of the outlet end (52) of the discharge port (50).
  • a cross sectional area Ao of the virtual outlet side flow path (75) is expressed by Equation 5. Equation 5 is the same as Equation 02 described above.
  • Ao Lo ⁇ ho
  • the wetted perimeter length of the virtual outlet side flow path (75) is a sum of its upper peripheral length and its lower peripheral length.
  • the wetted perimeter length of the virtual outlet side flow path (75) is 2Lo.
  • the hydraulic diameter Do of the virtual outlet side flow path (75) is therefore expressed by Equation 6.
  • the hydraulic diameter of the actual outlet side flow path (70) is considered as being equal to the hydraulic diameter Do calculated by Equation 6. Equation 6 is the same as Equation 03 described above.
  • the peripheral length Lo of the outlet end (52) of the discharge port (50) is 30.1 mm.
  • the cross sectional area Ao and the hydraulic diameter Do of the virtual outlet side flow path (75) are a function of the reference lift amount ho.
  • FIG. 8 shows the cross sectional area Ao of the flow path and the hydraulic diameter Do thereof in each of the cases where the reference lift amount ho is 0.8 mm, 1.0 mm, 1.2 mm, 1.4 mm and 1.6 mm.
  • the reference lift amount ho of the valve body (61) of the discharge valve (60) is set to a value within a range defined by Formula 8. 0.25 ⁇ Do / Di ⁇ 0.5 Di / 8 ⁇ ho ⁇ Di / 4
  • FIG. 8 shows the hydraulic diameter Do of the outlet side flow path (70) and values of the hydraulic diameter rate Do/Di in each of the cases where the reference lift amount ho is 0.8 mm, 1.0 mm, 1.2 mm, 1.4 mm and 1.6 mm.
  • the hydraulic diameter rate Do/Di is 0.25 or more and 0.5 or less.
  • the hydraulic diameter rate Do/Di is larger than 0.5.
  • each of the cases where the reference lift amount ho is 0.8 mm, 1.0 mm, 1.2 mm and 1.4 mm is an embodiment of the present application, whereas the case in which the reference lift amount ho is 1.6 mm is not an embodiment of the present application, but a comparative example.
  • Equation 9 The values of the hydraulic diameter rate Do/Di shown in FIG. 8 were calculated using Equation 9 below. Equation 9 can be obtained by substituting Equation 1 to Equation 3 and Equation 6 for Do/Di.
  • the gas refrigerant discharged from the compressor mechanism (30) is ejected first from the outlet end (52) of the discharge port (50) to the valve body (61) of the discharge valve (60), and then collides with the front surface (61a) of the valve body (61) and changes its flow direction to spread around the outlet end (52) of the discharge port (50).
  • the vertical vortex shown in FIG. 9A is generated and disappears several times in one discharge process. As mentioned above, the vertical vortex interrupts a flow of the gas refrigerant that is about to flow out from the outlet side flow path (70). Thus, every time the vertical vortex is generated and disappears, a flow rate of the gas refrigerant flowing out from the outlet side flow path (70) changes.
  • FIG. 10B , FIG. 11B , FIG. 12B and FIG. 13B show changes in amass flow rate (that is, a discharge flow rate) of the gas refrigerant discharged from the discharge port (50) of the compressor mechanism (30).
  • a discharge flow rate that is, a discharge flow rate
  • the discharge flow rate rapidly increases when the discharge valve (60) starts to separate from the outlet end (52) of the discharge port (50) at a point where a rotation angle of the drive shaft (23) is around 230°.
  • the discharge flow rate shows a maximum value at a point where the rotation angle of the drive shaft (23) is around 250°.
  • the discharge flow rate relatively significantly changes in spite of the fact that the lift amount of the valve body (61) is approximately uniform.
  • the changes in the discharge flow rate are as small as possible since such changes lead to vibrations of the compressor (10) and noise.
  • the range of the discharge flow rate in the discharge process is smaller in each of the cases where the reference lift amount ho is 0.8 mm, 1.0 mm, 1.2 mm and 1.4 mm, than in the case where the reference lift amount ho is 1.6 mm. Further, the range of the discharge flow rate in the discharge process is reduced as the reference lift amount ho becomes smaller.
  • the reference lift amount ho of the valve body (61) of the discharge valve (60) is determined such that the hydraulic diameter rate Do/Di is 0.5 or less.
  • the valve body (61) When the discharge valve (60) is opened/closed, the valve body (61) is elastically deformed, causing the end portion of the valve body (61) to move.
  • the longer traveling distance of the valve body (61) requires longer time to open/close the discharge valve (60).
  • a phenomenon referred to as a "delay-in-closing phenomenon” occurs in which the valve body (61) is separated from the outlet end (52) of the discharge port (50) even at a moment when the discharge valve (60) is supposed to be closed.
  • the lift amount of the valve body (61) is about 0.6 mm even at a moment when the rotation angle of the drive shaft (23) reaches 360°.
  • the compression chamber (36) in an early stage of the compression process communicates with the internal space of the casing (11) through the discharge port (50), and as a result, the high-pressure gas refrigerant in the internal space of the casing (11) flows back to the compression chamber (36) through the discharge port (50).
  • the delay-in-closing phenomenon occurs, the mass flow rate of the refrigerant discharged from the compressor mechanism (30) per unit time is reduced, and that leads to a reduction in efficiency of the compressor (10).
  • the reference lift amount ho of the valve body (61) of the discharge valve (60) is as small as possible.
  • the reference lift amount ho of the valve body (61) of the discharge valve (60) is determined such that the hydraulic diameter rate Do/Di is 0.25 or more.
  • the reference lift amount ho of the valve body (61) of the discharge valve (60) is determined such that the hydraulic diameter rate Do/Di is 0.25 or more and 0.5 or less. It is thus possible to reduce time necessary for opening/closing the valve body (61) by reducing the reference lift amount ho of the valve body (61), without increasing the pressure loss of the refrigerant (the discharged refrigerant) discharged from the compressor mechanism (30). If the valve body (61) is opened/closed with less time, the amount of the refrigerant flowing back to the compression chamber (36) due to a delay in closing the valve body (61) is reduced.
  • the height H and the width W of the chamfered portion (56) satisfy the relationship of 0 ⁇ H/W ⁇ 0.5. That is, in the present embodiment, the chamfered portion (56) has a relatively gentle inclination.
  • the area (i.e., the pressure receiving area) of the portion of the front surface (61a) of the valve body (61) to which pressure is applied from the discharge port (50) can be increased, and an increase in the volume of the discharge port (50) due to the provision of the chamfered portion (56) can be reduced.
  • the efficiency reduction of the compressor (10) due to an increase in the dead volume can be reduced, and the efficiency of the compressor (10) can be improved due to a reduction in loss by overcompression.
  • the reference lift amount ho of the valve body (61) of the discharge valve (60) such that the hydraulic diameter rate Do/Di is 0.25 or more and 0.4 or less.
  • valve body (61) If the valve body (61) is separated from the seat portion (55) at the point when the rotation angle of the drive shaft (23) reaches 360°, the internal space of the casing (11) communicates with the suction port (42) through the discharge port (50) and the compression chamber (36), and this may result in an excess amount of refrigerant flowing back to the compression chamber (36) from the internal space of the casing (11).
  • Vmin shown in FIG. 14 is a lower limit of the amount of refrigerant flowing back to the compression chamber (36). That is, the amount of refrigerant flowing back to the compression chamber (36) cannot be reduced to zero because of the structure of the compressor (10). For example, in reality, it is impossible to reduce the volume of the discharge port (50) to zero, and the amount exceeding the lower limit Vmin is an amount of refrigerant flowing back to the compression chamber (36) which can be reduced. As shown in FIG. 14 , the amount of refrigerant flowing back to the compression chamber (36) which can be reduced is ⁇ V 1 in the case where the hydraulic diameter rate Do/Di is 0.53, and ⁇ V 2 in the case where the hydraulic diameter rate Do/Di is 0.4.
  • ⁇ V 2 is less than half ⁇ V 1 ( ⁇ V 2 ⁇ ⁇ V 1 /2).
  • the cross sectional area Ao of the virtual outlet side flow path (75) is substantially equal to the area Ai of the inlet end (51) of the discharge port (50).
  • the cross sectional area Ao of the virtual outlet side flow path (75) is smaller than the area Ai of the inlet end (51) of the discharge port (50).
  • the reference lift amount ho of the valve body (61) of the discharge valve (60) such that the cross sectional area Ao of the virtual outlet side flow path (75) is less than or equal to the area Ai of the inlet end (51) of the discharge port (50) (Ao ⁇ Ai).
  • the cross sectional area of the main pass (53) of the discharge port (50) may be gradually increased from the inlet end (51) to the outlet end (52) of the discharge port (50).
  • the wall surface forming the main pass (53) of the discharge port (50) is a conical surface about the center line CL of the discharge port (50).
  • the longer diameter length D 12 of the upper end of the main pass (53) is longer than the longer diameter length D 11 of the lower end of the main pass (53), and the shorter diameter length D 22 of the upper end of the main pass (53) is longer than the longer diameter length D 21 of the lower end of the main pass (53).
  • the chamfered portion (56) may be omitted.
  • the shape of the cross section of the flow path of the discharge port (50) according to the present variation is a uniform oblong shape from the inlet end (51) to the outlet end (52) of the discharge port (50).
  • the cross sectional shape of the discharge port (50) may be an ellipse.
  • the front head (31) is provided with a chamfered portion (56) around the entire periphery (52a) of the outlet end (52) of the discharge port (50).
  • the height H and the width W of the chamfered portion (56) of the present variation are respectively uniform around the entire periphery (52a) of the outlet end (52) of the discharge port (50).
  • the cross sectional shape of the discharge port (50) of the present variation is not limited to an accurate ellipse having two focus points, but may be a shape whose periphery is formed by a curve and which looks like an ellipse at a glance.
  • the compressor mechanism (30) of the compressor (10) of the present embodiment may be a rotary fluid machine of rolling piston type, in which the blade (43) is formed independently from the piston (38).
  • the flat plate-like blade (43) is fitted in a blade groove extending in the radius direction of the cylinder (32) so as to be capable of moving to and fro, and the bushes (41) are omitted.
  • the blade (43) is pressed against the outer circumferential surface (39) of the piston (38) by a spring (44), and the end portion of the blade (43) slides with the outer circumferential surface (39) of the piston (38).
  • the cross sectional shape of the discharge port (50) is a circle.
  • the cross sectional shape of the discharge port (50) of the present variation may be an oblong shown in FIG. 6 or an ellipse shown in FIG. 17 .
  • the present invention is useful for a compressor having a discharge valve.

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Claims (6)

  1. Kompressor mit einem feststehenden Element (45), das eine Kompressionskammer (36) bildet, und einem beweglichen Element (38), das gedreht wird und ein Volumen der Kompressionskammer (36) ändert, wobei der Kompressor konfiguriert ist, um ein Fluid in die Kompressionskammer (36) zu saugen und das Fluid zu komprimieren, wobei
    das feststehende Element (45) mit einer Auslassöffnung (50), die das feststehende Element (45) durchdringt und das Fluid aus der Kompressionskammer (36) herausführt, und mit einem Auslassventil (60) versehen ist, das die Auslassöffnung (50) öffnet/verschließt,
    das Auslassventil (60) einen Ventilkörper (61) aufweist, der die Auslassöffnung (50) durch Abdecken eines Auslassendes (52) der Auslassöffnung (50) verschließt und die Auslassöffnung (50) durch Anheben vom Auslassende (52) der Auslassöffnung (50) öffnet,
    eine Fläche eines Einlassendes (51) der Auslassöffnung (50) Ai ist; eine Umfangslänge des Einlassendes (51) Li ist und ein hydraulischer Durchmesser des Einlassendes (51) definiert ist durch Di = 4(Ai/Li),
    eine Umfangslänge des Auslassendes (52) der Auslassöffnung (50) Lo ist; eine Referenzhubhöhe des Ventilkörpers (61) ho ist; eine Querschnittsfläche eines auslassseitigen Strömungswegs (70), der zwischen dem Auslassende (52) der Auslassöffnung (50) und dem Ventilkörper (61) gebildet ist, definiert ist durch Ao = Lo × ho; und ein hydraulischer Durchmesser des auslassseitigen Strömungswegs (70) definiert ist durch Do = 4 (Ao/2 Lo),
    dadurch gekennzeichnet, dass ein Verhältnis (Do/Di) des hydraulischen Durchmessers Do des auslassseitigen Strömungswegs (70) zum hydraulischen Durchmesser Di des Einlassendes (51) der Auslassöffnung (50) 0,5 oder weniger beträgt.
  2. Kompressor nach Anspruch 1, wobei das Verhältnis (Do/Di) des hydraulischen Durchmessers Do des auslassseitigen Strömungswegs (70) zum hydraulischen Durchmesser Di des Einlassendes (51) der Auslassöffnung (50) 0,4 oder weniger beträgt.
  3. Kompressor nach Anspruch 1 oder 2, wobei das Verhältnis (Do/Di) des hydraulischen Durchmessers Do des auslassseitigen Strömungswegs (70) zum hydraulischen Durchmesser Di des Einlassendes (51) der Auslassöffnung (50) 0,25 oder weniger beträgt.
  4. Kompressor nach einem der Ansprüche 1-3, wobei das feststehende Element (45) mit einem abgeschrägten Abschnitt (56) entlang des gesamten Umfangs des Auslassendes (52) der Auslassöffnung (50) versehen ist.
  5. Kompressor nach Anspruch 4, wobei eine Höhe H des abgeschrägten Abschnitts (56) in einer axialen Richtung der Auslassöffnung (50) und eine Breite W des abgeschrägten Abschnitts (56) in einer zur axialen Richtung der Auslassöffnung (50) orthogonalen Richtung eine Beziehung von 0<H/W<0,5 erfüllt.
  6. Kompressor nach einem der Ansprüche 1-5, wobei eine Querschnittsgestalt der Auslassöffnung (50) länglich oder ellipsenförmig ist.
EP13823006.5A 2012-07-25 2013-07-23 Kondensator Active EP2886864B1 (de)

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JP2012165128 2012-07-25
JP2012288002A JP5429353B1 (ja) 2012-07-25 2012-12-28 圧縮機
PCT/JP2013/004489 WO2014017081A1 (ja) 2012-07-25 2013-07-23 圧縮機

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JP2018091165A (ja) 2016-11-30 2018-06-14 三菱重工サーマルシステムズ株式会社 圧縮機
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JP7032864B2 (ja) * 2017-03-22 2022-03-09 三菱重工サーマルシステムズ株式会社 圧縮機
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JP7108222B1 (ja) * 2021-09-30 2022-07-28 ダイキン工業株式会社 圧縮機および冷凍装置

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ES2672321T3 (es) 2018-06-13
CN104487708B (zh) 2016-01-20
WO2014017081A1 (ja) 2014-01-30
EP2886864A4 (de) 2016-09-21
EP2886864A1 (de) 2015-06-24
JP5429353B1 (ja) 2014-02-26
JP2014040827A (ja) 2014-03-06
US20150211508A1 (en) 2015-07-30
CN104487708A (zh) 2015-04-01

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