WO2020153705A1 - Compresseur de type à plateau oscillant - Google Patents

Compresseur de type à plateau oscillant Download PDF

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Publication number
WO2020153705A1
WO2020153705A1 PCT/KR2020/001001 KR2020001001W WO2020153705A1 WO 2020153705 A1 WO2020153705 A1 WO 2020153705A1 KR 2020001001 W KR2020001001 W KR 2020001001W WO 2020153705 A1 WO2020153705 A1 WO 2020153705A1
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WO
WIPO (PCT)
Prior art keywords
flow path
discharge flow
swash plate
chamber
discharge
Prior art date
Application number
PCT/KR2020/001001
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English (en)
Korean (ko)
Inventor
유준하
서민호
손은기
윤제수
이현우
정유철
최형인
Original Assignee
한온시스템 주식회사
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.)
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Publication date
Application filed by 한온시스템 주식회사 filed Critical 한온시스템 주식회사
Priority to CN202080006269.4A priority Critical patent/CN113056608B/zh
Publication of WO2020153705A1 publication Critical patent/WO2020153705A1/fr

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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
    • 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
    • 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
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a

Definitions

  • the present invention relates to a swash plate type compressor, and more particularly, to a swash plate type compressor that can adjust the inclination angle of the swash plate by adjusting the pressure of the crankcase provided with the swash plate.
  • a compressor that serves to compress refrigerant in a vehicle cooling system has been developed in various forms, and in such a compressor, a configuration for compressing refrigerant performs compression while reciprocating and rotating while compressing while reciprocating. There is a rotating type.
  • the reciprocating type includes a crank type that transmits the driving force of the drive source to a plurality of pistons using a crank, a swash plate type that transmits to a rotating shaft provided with a swash plate, and a wobble plate type that uses a wobble plate.
  • a crank type that transmits the driving force of the drive source to a plurality of pistons using a crank
  • a swash plate type that transmits to a rotating shaft provided with a swash plate
  • a wobble plate type that uses a wobble plate.
  • vane rotary type using vane
  • scroll type using orbiting scroll and fixed scroll.
  • the swash plate type compressor is a compressor that compresses refrigerant by reciprocating a piston with a swash plate that rotates with a rotating shaft.
  • the refrigerant discharge amount is adjusted by adjusting the stroke of the piston by adjusting the inclination angle of the swash plate to improve the performance and efficiency of the compressor It is formed in a so-called variable dose mode to regulate.
  • FIG. 1 is a cross-sectional view showing a conventional swash plate type compressor of variable capacity.
  • the conventional swash plate type compressor the housing 100, the housing 100 having a bore 116, a suction chamber (S1), a discharge chamber (S3) and a crankcase (S4) Rotating shaft 200 rotatably supported, the swash plate 300 interlocked with the rotation shaft 200 and rotated inside the crankcase S4, interlocked with the swash plate 300 within the bore 116
  • a valve mechanism that reciprocates and communicates and shields the piston 400, the suction chamber S1, and the discharge chamber S3 with the compression chamber S2 forming the compression chamber S2 together with the bore 116.
  • Adjust the inclination angle of the swash plate 300 with respect to the 500 and the rotation axis 200 (the angle between the rotation axis 200 of the swash plate 300 and the normal line of the swash plate 300 based on the rotation center of the swash plate 300) It includes a tilt adjustment mechanism.
  • the inclination control mechanism, the inlet flow path (not shown) for guiding the refrigerant in the discharge chamber (S3) to the crankcase (S4) and the discharge for guiding the refrigerant in the crankcase (S4) to the suction chamber (S1) Includes Euro 800.
  • a pressure regulating valve for controlling the amount of refrigerant flowing into the inflow passage (not shown) from the discharge chamber S3 is formed.
  • An orifice hole 810 is formed in the discharge flow path 800 to depressurize the fluid passing through the discharge flow path 800.
  • the piston 400 is reciprocated within the bore 116 by converting the rotational motion of the swash plate 300 into a linear motion.
  • the compression chamber S2 communicates with the suction chamber S1 by the valve mechanism 500 and is connected to the discharge chamber S3. Shielded, the refrigerant in the suction chamber (S1) is sucked into the compression chamber (S2).
  • the compression chamber S2 is shielded from the suction chamber S1 and the discharge chamber S3 by the valve mechanism 500, and the The refrigerant in the compression chamber (S2) is compressed.
  • the compression chamber (S2) is shielded from the suction chamber (S1) by the valve mechanism 500 and communicates with the discharge chamber (S3), The refrigerant compressed in the compression chamber (S2) is discharged to the discharge chamber (S3).
  • the amount of refrigerant flowing into the inflow passage (not shown) from the discharge chamber S3 is adjusted by the pressure regulating valve (not shown) according to the required amount of refrigerant discharge, and the crank
  • the pressure of the seal S4 is adjusted, the pressure of the crankcase S4 applied to the piston 400 is adjusted, the stroke of the piston 400 is adjusted, and the inclination angle of the swash plate 300 is adjusted And the refrigerant discharge amount is adjusted.
  • the refrigerant in the crankcase (S4) is discharged to the suction chamber (S1) through the discharge flow path 800, but the suction chamber (S1) from the crankcase (S4) through the discharge flow path (800)
  • the amount of refrigerant flowing into the suction chamber (S1) through the inflow passage (not shown) from the discharge chamber (S3) is greater than the amount of refrigerant discharged to the pressure of the crankcase (S4). Accordingly, the pressure of the crankcase S4 applied to the piston 400 is increased, the stroke of the piston 400 is reduced, the inclination angle of the swash plate 300 is reduced, and the refrigerant discharge amount is reduced. .
  • the piston 400 is a moment due to a differential pressure obtained by subtracting the pressure of the crankcase S4 from the pressure of the compression chamber S2 mainly applied to the piston 400.
  • the smaller the pressure of the crankcase S4 the more the inclination angle of the swash plate 300 is increased, the stroke of the piston 400 is increased, and the refrigerant discharge amount is increased.
  • the pressure of the crankcase S4 increases, the inclination angle of the swash plate 300 decreases, the stroke of the piston 400 decreases, and the refrigerant discharge amount decreases.
  • an object of the present invention is to provide a swash plate type compressor capable of improving operation delay due to liquid refrigerant during initial operation.
  • a housing having a bore, a suction chamber, a discharge chamber and a crank chamber; A rotating shaft rotatably mounted to the housing; A swash plate rotated with the rotating shaft; A piston interlocked with the swash plate to reciprocate inside the bore to form a compression chamber with the bore; A first discharge channel for guiding the refrigerant in the crankcase to the suction chamber; And a second discharge passage branched from the first discharge passage and guiding the refrigerant in the crankcase to the suction chamber.
  • the first discharge flow path may include a chamber located between an upstream portion of a first discharge flow path communicating with the crank chamber, a downstream portion of a first discharge flow path communicating with the suction chamber, and an upstream portion of the first discharge flow path and a downstream portion of the first discharge flow path.
  • the second discharge flow path may include an upstream portion of a second discharge flow path communicating with the chamber and a downstream portion of a second discharge flow path communicating with the suction chamber.
  • the second discharge flow path is radially outside from the first discharge flow path and may be formed on the side of the gravity direction based on the first discharge flow path.
  • a first orifice hole for reducing the pressure of the refrigerant passing through the first discharge flow path is formed in the first discharge flow path, and a second for reducing the pressure of the refrigerant passing through the second discharge flow path is formed in the second discharge flow path.
  • Orifice holes may be formed.
  • the first orifice hole may be formed coaxially with the rotation axis, and the second orifice hole may be formed at a position spaced apart from the first orifice hole in the rotational radial direction of the rotation axis.
  • the second orifice hole may be formed on the side of the gravity direction based on the first orifice hole.
  • the housing includes a cylinder block in which the bore is formed; A front housing which is coupled to one side of the cylinder block and on which the crankcase is formed; And a rear housing coupled to the other side of the cylinder block and on which the suction chamber and the discharge chamber are formed, the valve mechanism communicating and shielding the suction chamber and the discharge chamber between the cylinder block and the rear housing with the compression chamber. Is interposed, and the first orifice hole and the second orifice hole may be formed in the valve mechanism.
  • the rear housing may include a post extending from the inner wall surface of the rear housing to support the valve mechanism, and a communication path communicating the second orifice hole and the suction chamber may be formed in the post.
  • the communication path may be formed of a slot extending from a central portion of the front end surface of the post to an outer peripheral portion of the front end surface of the post.
  • the communication path may be formed as an inclined hole penetrating the post from the front end surface of the post to the outer peripheral surface of the post.
  • the post is formed of at least one, the communication passage is formed for each post, the second discharge passage and the second orifice hole may be formed to correspond to each communication passage.
  • the flow cross-sectional area of the first orifice hole is formed to be included within a range of 1.54 mm2 or more and 4.52 mm2 or less, and the sum of the flow cross-sectional area of the at least one second orifice hole may be formed to 125% or less of the flow cross-sectional area of the first orifice hole. have.
  • a housing having a bore, a suction chamber, a discharge chamber and a crank chamber; A rotating shaft rotatably mounted to the housing; A swash plate rotated with the rotating shaft; A piston interlocked with the swash plate to reciprocate inside the bore to form a compression chamber with the bore; A first discharge channel for guiding the refrigerant in the crankcase to the suction chamber; And a second discharge flow path that bypasses the first discharge flow path and guides the refrigerant in the crankcase to the suction chamber.
  • the second discharge flow path is radially outside from the first discharge flow path and may be formed on the side of the gravity direction based on the first discharge flow path.
  • the first discharge flow path may include a chamber located between an upstream portion of a first discharge flow path communicating with the crank chamber, a downstream portion of a first discharge flow path communicating with the suction chamber, and an upstream portion of the first discharge flow path and a downstream portion of the first discharge flow path.
  • the second discharge flow path may include an upstream portion of a second discharge flow path communicating with the crank chamber and a downstream portion of a second discharge flow path communicating with the suction chamber.
  • the swash plate type compressor includes a housing having a bore, a suction chamber, a discharge chamber, and a crank chamber; A rotating shaft rotatably mounted to the housing; A swash plate rotated with the rotating shaft; A piston interlocked with the swash plate to reciprocate inside the bore to form a compression chamber with the bore; A first discharge channel for guiding the refrigerant in the crankcase to the suction chamber; And a second discharge flow path branching from the first discharge flow path or bypassing the first discharge flow path to guide the refrigerant in the crankcase to the suction chamber, thereby improving operation delay due to liquid refrigerant during initial operation. have.
  • FIG. 1 is a cross-sectional view showing a conventional swash plate type compressor
  • Figure 2 is a cross-sectional view showing a swash plate type compressor according to an embodiment of the present invention
  • FIG. 3 is an enlarged view of part A of FIG. 2,
  • Figure 4 is a perspective view of Figure 3
  • Figure 5 is a perspective view showing the communication path of Figure 4,
  • FIG. 6 is a diagram showing the operation delay characteristics of the swash plate compressor of FIG. 2,
  • Figure 7 is a diagram showing the control characteristics of the swash plate compressor of Figure 2
  • FIG. 8 is a cross-sectional view showing a swash plate type compressor according to another embodiment of the present invention.
  • FIG. 10 is a perspective view of FIG. 9,
  • FIG. 11 is a perspective view showing the communication path of FIG. 10.
  • Figure 2 is a cross-sectional view showing a swash plate compressor according to an embodiment of the present invention
  • Figure 3 is an enlarged view of part A of Figure 2
  • Figure 4 is a perspective view of Figure 3
  • FIG. 7 is a diagram showing the control characteristics of the swash plate compressor of FIG.
  • the swash plate type compressor may include a housing 100 and a compression mechanism provided inside the housing 100 to compress refrigerant. .
  • the housing 100 includes a cylinder block 110 in which the compression mechanism is accommodated, a front housing 120 coupled to the front of the cylinder block 110, and a rear housing coupled to the rear of the cylinder block 110 ( 130).
  • a shaft 112 through which a rotating shaft 200 to be described later is inserted and a chamber 114 communicating with the shaft 112 are formed, and on the outer circumferential side of the cylinder block 110
  • the piston 400 to be described later is inserted and a bore 116 forming a compression chamber S2 together with the piston 400 to be described later is formed, and an inflow passage to be described later is provided between the contraction hole 112 and the bore 116.
  • a first discharge flow path 800 to be described later and a second discharge flow path 900 to be described later may be formed.
  • the shaft hole 112 and the chamber 114 may be formed in a cylindrical shape penetrating the cylinder block 110 along the axial direction of the cylinder block 110.
  • the bore 116 is a cylindrical shape penetrating the cylinder block 110 along the axial direction of the cylinder block 110 at a portion spaced apart radially outward of the cylinder block 110 from the shaft hole 112. Can be formed.
  • the bore 116 is formed of n pieces so that the compression chamber (S2) is n, and the n bore 116 is the circumferential direction of the cylinder block 110 around the contraction hole (112). Can be arranged accordingly.
  • the front housing 120 is fastened to the cylinder block 110 from the front to form a crankcase S4 together with the cylinder block 110.
  • the swash plate 300 to be described later may be accommodated in the crankcase S4.
  • the rear housing 130 may be fastened to the cylinder block 110 on the opposite side of the front housing 120 based on the cylinder block 110.
  • the rear housing 130 may include a suction chamber S1 in which refrigerant to be introduced into the compression chamber S2 is accommodated, and a discharge chamber S3 in which refrigerant discharged from the compression chamber S2 is accommodated.
  • a suction chamber S1 in which refrigerant to be introduced into the compression chamber S2 is accommodated
  • a discharge chamber S3 in which refrigerant discharged from the compression chamber S2 is accommodated.
  • the suction chamber S1 may be in communication with a refrigerant suction pipe (not shown) that guides the refrigerant to be compressed into the housing 100.
  • the discharge chamber S3 may communicate with a refrigerant discharge pipe (not shown) that guides the compressed refrigerant to the outside of the housing 100.
  • the rear housing 130 further includes a post 132 extending from an inner wall surface of the rear housing 130 to support the valve mechanism 500 to be described later to prevent deformation of the rear housing 130. can do.
  • the post 132 may include a communication path 920 communicating the second orifice hole 910 and the suction chamber S1, which will be described later, to simplify the structure and reduce costs.
  • the compressor mechanism sucks refrigerant from the suction chamber (S1) into the compression chamber (S2), compresses the sucked refrigerant in the compression chamber (S2), and discharges the compressed refrigerant from the compression chamber (S2). It may be formed to discharge to the seal (S3).
  • the compressor mechanism is rotatably mounted on the housing 100 and rotated by receiving rotational force from a driving source (for example, an engine of a vehicle) (not shown), and rotating the shaft 200 and the rotating shaft 200 It may be linked to the swash plate 300 is rotated in the interior of the crankcase (S4), the piston 400 is connected to the swash plate 300 to reciprocate in the interior of the bore 116.
  • a driving source for example, an engine of a vehicle
  • the rotating shaft 200 may be formed in a cylindrical shape extending in one direction.
  • the rotating shaft 200 is rotatably supported by one end is inserted into the shaft hole 112, the other end penetrates through the front housing 120 and protrudes to the outside of the housing 100 and the driving source ( (Not shown).
  • the swash plate 300 is formed in a disc shape, and may be inclined to the rotating shaft 200 in the crankcase S4.
  • the swash plate 300 is fastened to the rotating shaft 200 so that the inclination angle of the swash plate 300 is variable, which will be described later.
  • the piston 400 includes one end inserted into the bore 116 and the other end extending from the one end to the opposite side of the bore 116 and connected to the swash plate 300 in the crankcase S4. can do.
  • n pistons 400 may be provided to correspond to the bore 116.
  • the swash plate compressor according to the present embodiment further includes a valve mechanism 500 for communicating and shielding the suction chamber S1 and the discharge chamber S3 with the compression chamber S2, and the valve mechanism ( A first orifice hole 810 to be described later and a second orifice hole 910 to be described later may be formed in 500).
  • the swash plate type compressor according to the present embodiment may further include an inclination adjusting mechanism for adjusting the inclination angle of the swash plate 300 with respect to the rotating shaft 200.
  • the inclination adjustment mechanism, the swash plate 300 is fastened to the rotating shaft 200, but the inclination angle of the swash plate 300 is variably fastened to the rotating shaft 200 and rotated together with the rotating shaft 200
  • the rotor 600 and the swash plate 300 may include a sliding pin 700 connecting the rotor 600.
  • the inclination adjusting mechanism the inlet flow path for guiding the refrigerant in the discharge chamber (S3) to the crankcase (S4) so as to adjust the pressure of the crankcase (S4) to adjust the inclination angle of the swash plate (300).
  • the refrigerant in the crankcase (S4) branched from the first discharge flow path (800) and the first discharge flow path (800) for guiding the refrigerant in the crankcase (S4) to the suction chamber (S1) It may include a second discharge passage (900) for guiding to the suction chamber (S1).
  • the inflow passage (not shown) may extend through the valve mechanism 500 and the cylinder block 110 to extend from the discharge chamber S3 to the crankcase S4.
  • a pressure regulating valve for adjusting the opening amount of the inflow passage (not shown) may be formed in the inflow passage (not shown).
  • the pressure regulating valve (not shown) may be formed of a so-called mechanical valve (MCV) or an electronic valve (ECV).
  • MCV mechanical valve
  • ECV electronic valve
  • the first discharge flow path 800 penetrates through one side of the cylinder block 110, passes through the chamber 114, penetrates through one side of the valve mechanism 500, and the suction chamber from the crank chamber S4 ( It can be extended to S1). That is, the first discharge flow path 800 includes a first discharge flow path upstream portion 800a communicating with the crankcase S4, a first discharge flow path downstream portion 800b communicating with the suction chamber S1, and the The first discharge flow path may include a chamber 114 positioned between the upstream portion 800a and the first discharge flow path downstream portion 800b.
  • a first orifice hole 810 for depressurizing the refrigerant passing through the first discharge flow path 800 is formed in the first discharge flow path 800 to prevent the pressure in the suction chamber S1 from rising.
  • the first orifice hole 810 is formed in the downstream portion 800b of the first discharge passage, and may be formed in the valve mechanism 500 to facilitate manufacturing.
  • first orifice hole 810 and the rotating shaft 200 so that the refrigerant discharged from the first orifice hole 810 to the suction chamber S1 is uniformly distributed to the n compression chambers S2. It can be formed on the coaxial. That is, the first orifice hole 810 may be formed at the center side of the valve mechanism 500.
  • the second discharge passage 900 may be formed to extend from the chamber 114 to the suction chamber S1 through the other side of the cylinder block 110 and the other side of the valve mechanism 500. That is, the second discharge flow path 900 may include a second discharge flow path upstream portion 900a communicating with the chamber and a second discharge flow path downstream portion 900b communicating with the suction chamber S1.
  • a second orifice hole 910 for depressurizing the refrigerant passing through the second discharge flow path 900 is formed in the second discharge flow path 900 to prevent the pressure in the suction chamber S1 from rising. Can.
  • the second orifice hole 910 is formed in the downstream portion 900b of the second discharge flow path, and may be formed in the valve mechanism 500 to facilitate manufacturing.
  • the second orifice hole 910 is formed at a position spaced apart from the first orifice hole 810 in the rotational radial direction of the rotating shaft 200, as described below, below the crankcase S4. It may be preferable that the accumulated liquid refrigerant is formed on the side of the gravity direction based on the first orifice hole 810 so as to be quickly discharged to the suction chamber S1.
  • the second discharge flow path 900 is also formed on the side of the gravity direction based on the first discharge flow path 800 so that the liquid refrigerant of the crank chamber S4 is quickly discharged to the suction chamber S1. can do.
  • the rotating shaft 200 and the swash plate 300 may be rotated together.
  • the piston 400 may be reciprocated within the bore 116 by converting the rotational motion of the swash plate 300 into a linear motion.
  • the compression chamber S2 communicates with the suction chamber S1 by the valve mechanism 500 and is connected to the discharge chamber S3. Shielded, the refrigerant in the suction chamber (S1) can be sucked into the compression chamber (S2).
  • the compression chamber S2 is shielded from the suction chamber S1 and the discharge chamber S3 by the valve mechanism 500, and the The refrigerant in the compression chamber (S2) can be compressed.
  • the compression chamber (S2) is shielded from the suction chamber (S1) by the valve mechanism 500 and communicates with the discharge chamber (S3), The refrigerant compressed in the compression chamber S2 may be discharged to the discharge chamber S3.
  • the amount of refrigerant flowing into the inflow passage (not shown) from the discharge chamber S3 is adjusted by the pressure regulating valve (not shown) according to the required amount of refrigerant discharge.
  • the pressure of the crankcase (S4) is adjusted, the pressure of the crankcase (S4) applied to the piston 400 is adjusted, the stroke of the piston 400 is adjusted, the swash plate (300) The inclination angle is adjusted, and the refrigerant discharge amount can be adjusted.
  • the amount of refrigerant flowing from the discharge chamber (S3) to the inflow passage (not shown) is increased by the pressure control valve (not shown), and through the inflow passage (not shown)
  • the amount of refrigerant flowing into the crankcase (S4) is increased, so the pressure of the crankcase (S4) can be increased.
  • the refrigerant in the crankcase (S4) is discharged to the suction chamber (S1) through the first discharge flow path (800) and the second discharge flow path (900), but the first in the crankcase (S4) From the discharge chamber (S3) to the suction chamber (S1) from the discharge chamber (S3) than the amount of refrigerant discharged to the suction chamber (S1) through the discharge flow path (800) and the second discharge flow path (900)
  • the amount of refrigerant flowing in may be large, so the pressure in the crankcase (S4) may be increased. Accordingly, the pressure of the crankcase S4 applied to the piston 400 is increased, the stroke of the piston 400 is reduced, the inclination angle of the swash plate 300 is reduced, and the refrigerant discharge amount is reduced. Can.
  • the amount of refrigerant flowing into the inflow passage (not shown) from the discharge chamber (S3) is reduced by the pressure control valve (not shown), and through the inflow passage (not shown)
  • the amount of refrigerant flowing into the crankcase (S4) is reduced, so that the pressure of the crankcase (S4) can be reduced.
  • the swash plate type compressor according to the present embodiment the first discharge passage 800 having the first orifice hole 810 as well as the second discharge passage 900 having the second orifice hole 910 By including, it is possible to eliminate the operation delay during the initial operation while preventing freezing of the evaporator connected to the swash plate type compressor.
  • the flow cross-sectional area of the entire orifice hole may be increased. Accordingly, during the initial operation, the liquid refrigerant of the crankcase S4 is smoothly and quickly discharged to the suction chamber S1, and the operation delay can be improved as shown in FIG. 6. That is, in FIG.
  • the first sample is a swash plate compressor having one orifice hole having a flow cross-sectional area of 2.01 mm 2, which corresponds to a conventional swash plate type compressor, and the second to fifth samples have a flow cross-sectional area of 2.01 mm 2
  • a swash plate compressor including a first orifice hole 810 and a second orifice hole 910 having a flow cross-sectional area of 0.54 mm2, 1.14 mm2, 1.8 mm2, 2.52 mm2, which corresponds to the swash plate type compressor according to the present embodiment. It can be seen that the operation delay time of the first sample takes approximately 43 seconds, while the operation delay time of the second sample to the fifth sample takes approximately 20 seconds to 39 seconds.
  • the first discharge passage 800 and the first orifice A method of forming only the hole 810 but increasing the flow cross-sectional area of the first orifice hole 810 may be considered. That is, a method of increasing the flow cross-sectional area of the orifice hole in a conventional swash plate type compressor may be considered. Even in this case, the operation delay time can be improved. That is, in FIG.
  • the sixth sample is a swash plate compressor having one orifice hole equal to (3.81 mm 2) of the flow sectional area of the entire orifice hole of the fourth sample, which increases the flow sectional area of the orifice hole in a conventional swash plate compressor. It can be confirmed that the operation delay time of the sixth sample is about 24 seconds.
  • the second discharge flow path 900 and the second orifice hole 910 are additionally provided (for the second to fifth samples), the second discharge flow path 900 ) And the flow resistance of the second orifice hole 910, as shown in FIG. 7, the change in the control characteristics is small, the refrigerant discharge amount is less than the previously intended value, and freezing occurs in the evaporator. Can be prevented. That is, an increase in the compressor maximum capacity operating area is suppressed, so that the occurrence of compressor cycling can be reduced.
  • the flow cross-sectional area of the first orifice hole 810 and the flow cross-sectional area of the second orifice hole 910 are determined in a predetermined range. It may be desirable to form. That is, the flow cross-sectional area of the first orifice hole 810 is formed to be included within a range of 1.54 mm 2 or more and 4.52 mm 2 or less, and the flow cross-sectional area of the second orifice hole 910 is the flow of the first orifice hole 810. It may be desirable to form less than 125% of the cross-sectional area.
  • the second discharge flow path 900, the second orifice hole 910, and the communication path 920 are each formed as one, but are not limited thereto. That is, for example, the post 132 is formed of at least one, the communication path 920 is formed for each post 132, the second discharge flow path 900 and the second orifice hole 910 May be formed to correspond to each communication path 920. In this case, more effectively, it is possible to improve the operation delay during initial operation while preventing freezing of the evaporator.
  • the flow cross-sectional area of the first orifice hole 810 is formed to be included in a range of 1.54 mm2 or more and 4.52 mm2 or less, and the sum of the flow cross-sectional areas of the at least one second orifice hole 910 is the first orifice hole It may be preferably formed to be included within a range of 125% or less of the flow cross-sectional area of 810.
  • the second discharge flow path 900 is branched from the first discharge flow path 800, but as shown in FIGS. 8 to 11, the second discharge flow path 900 is the first discharge flow path ( 800) may be formed to bypass the first discharge flow path 800 to guide the refrigerant in the crankcase S4 to the suction chamber S1. That is, the second discharge flow path 900 includes a second discharge flow path upstream portion 900a communicating with the crankcase S4 and a second discharge flow path downstream portion 900b communicating with the suction chamber S1. can do.
  • the communication path 920 is formed of a slot extending from the center of the front end surface of the post 132 to the outer circumference of the front end surface of the post 132 to facilitate manufacturing. 11, the communication path 920 may be formed as an inclined hole penetrating the post 132 from a front end surface of the post 132 to an outer peripheral surface of the post 132.

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  • Engineering & Computer Science (AREA)
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  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)

Abstract

La présente invention concerne un compresseur de type à plateau oscillant, comprenant : un boîtier comprenant un alésage, une chambre d'aspiration, une chambre de refoulement et une chambre de vilebrequin; un arbre rotatif monté rotativement dans le boîtier; un plateau oscillant tournant conjointement avec l'arbre rotatif; un piston qui est verrouillé avec le plateau oscillant de manière à effectuer un mouvement de va-et-vient à l'intérieur de l'alésage, et qui forme une chambre de compression conjointement avec l'alésage; une première trajectoire de refoulement pour guider un réfrigérant dans la chambre de vilebrequin vers la chambre d'aspiration; et une seconde trajectoire de refoulement ramifiée à partir de la première trajectoire de refoulement ou contournant la première trajectoire de refoulement de façon à guider le réfrigérant dans la chambre de vilebrequin vers la chambre d'aspiration. En conséquence le compresseur de type à plateau oscillant peut atténuer un retard de fonctionnement provoqué par un réfrigérant liquide durant une opération initiale.
PCT/KR2020/001001 2019-01-25 2020-01-21 Compresseur de type à plateau oscillant WO2020153705A1 (fr)

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CN202080006269.4A CN113056608B (zh) 2019-01-25 2020-01-21 斜盘式压缩机

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KR10-2019-0009853 2019-01-25
KR1020190009853A KR20200092667A (ko) 2019-01-25 2019-01-25 사판식 압축기

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010048096A (ja) * 2008-08-19 2010-03-04 Toyota Industries Corp 車両用空調装置
JP2012207567A (ja) * 2011-03-29 2012-10-25 Toyota Industries Corp 可変容量型斜板式圧縮機
KR20150104995A (ko) * 2014-03-07 2015-09-16 한온시스템 주식회사 가변 사판식 압축기의 오일 분리 장치
US20170122300A1 (en) * 2014-06-27 2017-05-04 Valeo Japan Co., Ltd. Variable displacement swash plate compressor
KR20180101659A (ko) * 2017-03-02 2018-09-13 학교법인 두원학원 용량 가변형 사판식 압축기

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009209910A (ja) * 2008-03-06 2009-09-17 Toyota Industries Corp 斜板式圧縮機
KR101790777B1 (ko) 2011-03-03 2017-10-27 학교법인 두원학원 용량가변형 사판식 압축기

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010048096A (ja) * 2008-08-19 2010-03-04 Toyota Industries Corp 車両用空調装置
JP2012207567A (ja) * 2011-03-29 2012-10-25 Toyota Industries Corp 可変容量型斜板式圧縮機
KR20150104995A (ko) * 2014-03-07 2015-09-16 한온시스템 주식회사 가변 사판식 압축기의 오일 분리 장치
US20170122300A1 (en) * 2014-06-27 2017-05-04 Valeo Japan Co., Ltd. Variable displacement swash plate compressor
KR20180101659A (ko) * 2017-03-02 2018-09-13 학교법인 두원학원 용량 가변형 사판식 압축기

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CN113056608A (zh) 2021-06-29
KR20200092667A (ko) 2020-08-04
CN113056608B (zh) 2023-03-24

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