US20030113211A1 - Piston type compressor - Google Patents

Piston type compressor Download PDF

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Publication number
US20030113211A1
US20030113211A1 US10/292,043 US29204302A US2003113211A1 US 20030113211 A1 US20030113211 A1 US 20030113211A1 US 29204302 A US29204302 A US 29204302A US 2003113211 A1 US2003113211 A1 US 2003113211A1
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US
United States
Prior art keywords
rotary valve
valve
suction
drive shaft
accommodating chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US10/292,043
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English (en)
Inventor
Takahiro Moroi
Tomoji Tarutani
Masahiro Kawaguchi
Noriyuki Shintoku
Masaki Ota
Hisato Kawamura
Shigeki Kawachi
Yoshinori Inoue
Akio Saiki
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Toyota Industries Corp
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Toyota Industries Corp
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Filing date
Publication date
Application filed by Toyota Industries Corp filed Critical Toyota Industries Corp
Assigned to KABUSHIKI KAISHA TOYOTA JIDOSHOKKI reassignment KABUSHIKI KAISHA TOYOTA JIDOSHOKKI ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: INOUE, YOSHINORI, KAWACHI, SHIGEKI, KAWAGUCHI, MASAHIRO, KAWAMURA, HISATO, MOROI, TAKAHIRO, OTA, MASAKI, SAIKI, AKIO, SHINTOKU, NORIYUKI, TARUTANI, TOMOJI
Publication of US20030113211A1 publication Critical patent/US20030113211A1/en
Abandoned legal-status Critical Current

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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
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1054—Actuating elements
    • F04B27/1063—Actuating-element bearing means or driving-axis bearing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1009—Distribution members
    • F04B27/1018—Cylindrical distribution members

Definitions

  • the present invention relates to a piston type compressor for compressing gas by reciprocating movement of a piston.
  • a suction valve of a reed valve type is generally used for the piston type compressor.
  • a suction stroke of the piston causes a reduction in a pressure of a compression chamber.
  • the suction valve of the reed valve type is opened by a difference between the reduced pressure of the compression chamber and a pressure of a suction pressure region to permit suction of gas from the suction pressure region into the compression chamber.
  • a drive shaft 94 is rotatably supported on a housing 91 of a compressor 90 through rolling bearings 95 a and 95 b.
  • a valve accommodating chamber 96 for rotatably accommodating a rotary valve 97 is formed in a position coaxial to the drive shaft 94 .
  • a suction communicating passage 98 communicated with a compression chamber 99 is opened on the inner surface of the valve accommodating chamber 96 .
  • the rotary valve 97 is fixed to the drive shaft 94 so as to be integrally rotated.
  • a suction guiding groove 100 always communicated with a suction pressure region is formed on the outer surface of the rotary valve 97 .
  • the rotary valve 97 can connect or disconnect the suction guiding groove 100 to or from the suction communicating passage 98 in accordance with its rotational position. Especially, the rotary valve 97 connects the suction guiding groove 100 to the suction communicating passage 98 during a suction stroke of a piston to permit suction of gas from the suction pressure region into the compression chamber 99 .
  • the drive shaft 94 is supported on the housing 91 through the rolling bearings 95 a and 95 b.
  • the rolling bearings are complex in structure, and high-precision finishing is required, consequently increasing manufacturing costs. Costs of the compressor 90 that uses the rolling bearings 95 a and 95 b are inevitably increased.
  • core misalignment occurs because of an error in positional accuracy between the inner surface of the valve accommodating chamber 96 and an inner surface of each of accommodating chambers for accommodating the rolling bearing 95 a and 95 b in the housing 91 . Consequently, there is a possibility that galling may occur between the outer surface of the rotary valve 97 and the inner surface of the valve accommodating chamber 96 .
  • the accommodating chamber 96 and the accommodating chambers of the rolling bearings 95 a and 95 b must all be machined with high precision.
  • the compressor that employs the rolling bearings not only costs of the rolling bearings but also manufacturing costs of the compressor for housing the rolling bearings are high.
  • Such compressor as an end product is inevitably expensive.
  • a rotary valve 102 is integrally formed in the end of a drive shaft 101 .
  • slide bearings are arranged on the inner surface of a valve accommodating chamber 105 . That is, supporting of the drive shaft 101 by a cylinder block 106 is carried out through the rotary valve 102 and the slide bearings 103 and 104 .
  • the slide bearing 104 is provided between the outer surface of the rotary valve 102 and the inner surface of the valve accommodating chamber 105 , in other words, between a suction guiding groove 107 of the rotary valve 102 and a suction communicating passage 108 of the cylinder block 106 . Accordingly, in order to increase compression efficiency of a compressor, leakage of gas must be prevented both between the outer surface of the rotary valve 102 and the slide bearing 104 and between the slide bearing 104 and the inner surface of the valve accommodating chamber 105 . Therefore, it is necessary to machine the valve accommodating chamber 105 , into which the slide bearing 104 is inserted, and the inner surface of the slide bearing 104 , into which the rotary valve 102 is inserted, with high precision. This requirement increases costs of the compressor.
  • An object of the present invention is to provide a piston type compressor guaranteed for prevention of noise generated during use, and good use.
  • Another object of the present invention is to provide an inexpensive compressor.
  • Still another object of the present invention is to provide a compressor having excellent compression efficiency.
  • a piston type compressor includes a drive shaft rotatably supported on a housing.
  • the housing includes a cylinder block.
  • the cylinder block includes a cylinder bore and a valve accommodating chamber. Reciprocation of a piston operably connected to the drive shaft in the corresponding cylinder bore changes the volume of a compression chamber in the cylinder bore to compress gas supplied from a first region, on which a suction pressure acts, to the compression chamber. The compressed gas is sent to a second region, on which a discharge pressure acts.
  • the compressor includes a rotary valve accommodated in the valve accommodating chamber.
  • the rotary valve rotates integrally with the drive shaft to selectively open or close a passage of gas from the first pressure region to the compression chamber.
  • the rotary valve has a substantially cylindrical shape and an outer surface.
  • the valve accommodating chamber has a circular cross-section and an inner surface. The outer surface and the inner surface constitute slide bearing surfaces for receiving a radial load applied to the drive shaft by sliding on each other.
  • FIG. 1 is a vertical sectional view of a piston type variable displacement compressor.
  • FIG. 2 is a partially enlarged side view of a rotary valve of the compressor of FIG. 1.
  • FIG. 3 is a transverse sectional view of a portion in the vicinity of the rotary valve taken along the line 1 - 1 of FIG. 1.
  • FIG. 4 is a transverse sectional view of a portion in the vicinity of a rotary valve according to a second embodiment.
  • FIG. 5 is a vertical sectional view of a portion in the vicinity of a rotary valve according to a third embodiment.
  • FIG. 6 is a vertical sectional view of a portion in the vicinity of a rotary valve according to a fourth embodiment.
  • FIG. 7 is a vertical sectional view of a piston type variable displacement compressor according to a fifth embodiment.
  • FIG. 8 is a vertical sectional view of a portion in the vicinity of a rotary valve according to another example of FIG. 6.
  • FIG. 9 is a vertical sectional view of a portion in the vicinity of a rotary valve according to yet another example of FIG. 6.
  • FIG. 10 is a vertical sectional view of a double-head piston type compressor.
  • FIG. 11 is a partial vertical sectional view of another embodiment of the compressor of FIG. 10.
  • FIG. 12 is a vertical sectional view of a compressor according to the prior art.
  • FIG. 13 is a vertical sectional view of a compressor according to the prior art.
  • FIG. 1 left and right sides respectively show front and rear portions of a compressor.
  • a housing of the piston type variable displacement compressor (simply referred to as a compressor, hereinafter) includes a cylinder block 11 , a front housing 12 and a rear housing 14 .
  • the cylinder block 11 is made of an aluminum-series metallic material in order to reduce weight of the compressor.
  • the front housing 12 is coupled to the front end of the cylinder block 11 .
  • the rear housing 14 is coupled through a valve plate 13 to the rear end of the cylinder block 11 .
  • a crank chamber 15 is defined by the cylinder block 11 and the front housing 12 .
  • a drive shaft 16 is rotatably arranged in the crank chamber 15 .
  • the drive shaft 16 is made of an iron-series metallic material.
  • the drive shaft 16 is operably connected to an engine (not shown) as a driving source for traveling a vehicle, and rotated by receiving power from the engine.
  • a lug plate 21 is fixed onto the drive shaft 16 in the crank chamber 15 so as to be integrally rotated.
  • a swash plate 23 is housed in the crank chamber 15 .
  • the swash plate 23 is supported on the drive shaft 16 so as to slide and tilt.
  • a hinge mechanism 24 is provided between the lug plate 21 and the swash plate 23 . Accordingly, the swash plate 23 can be rotated integrally with the lug plate 21 and the drive shaft 16 by hinge connection with the lug plate 21 through the hinge mechanism 24 , and support by the drive shaft 16 .
  • the swash plate 23 can also tilt with respect to the drive shaft 16 , and slide in an axial direction of the drive shaft 16 .
  • a plurality of cylinder bores 11 a are formed in the cylinder block 11 .
  • the cylinder bores 11 a are formed to surround a rear end of the drive shaft 16 .
  • a single-head piston 25 is housed to be reciprocated in each cylinder bore 11 a. Openings on front and rear sides of the cylinder bore 11 a are closed by the valve plate 13 and the piston 25 .
  • the cylinder bore 11 a defines a compression chamber 26 changed in volume in accordance with the reciprocation of the piston 25 .
  • Each piston 25 is retained on the outer peripheral portion of the swash plate 23 through shoes 27 . Thus, rotation of the swash plate 23 accompanying rotation of the drive shaft 16 is converted through the shoes 27 into reciprocation of the piston 25 .
  • a suction chamber 28 and a discharge chamber 29 are defined in the rear housing 14 .
  • the suction chamber 28 is formed in the center of the rear housing 14 .
  • the discharge chamber 29 is formed to surround the outer surface of the suction chamber 28 .
  • An discharge port 32 and a discharge valve 33 are formed in the valve plate 13 .
  • the discharge port 32 communicates the compression chamber 26 and the discharge chamber 29 with each other.
  • the discharge valve 33 is a reed valve for selectively opening/closing the discharge port 32 .
  • a suction valve mechanism 35 equipped with a rotary valve 41 is provided in the cylinder block 11 .
  • a bleed passage 36 and a supply passage 37 is formed in the housing of the compressor.
  • the bleed passage 36 connects the crank chamber 15 with the suction chamber 28 .
  • the supply passage 37 connects the discharge chamber 29 with the crank chamber 15 .
  • a control valve 38 is provided in the supply passage 37 .
  • the supply passage 37 is an electromagnetic valve.
  • Varying the opening size of the control valve 38 controls the balance of the amount of incoming high-pressure discharge gas, which flows from the discharge chamber 29 through the supply passage 37 to the crank chamber 15 , and the amount of outgoing gas, which flows from the crank chamber 15 through the bleed passage 36 to the suction chamber 28 .
  • the internal pressure of the crank chamber 15 is determined.
  • the change in the internal pressure of crank chamber 15 cause the difference between the internal pressure of the crank chamber 15 and the internal pressure of the compression chamber 26 via the piston 25 to change. Then, Thus, the inclination angle of the swash plate 23 is varied and piston stroke, or the compressor displacement, is adjusted.
  • a valve accommodating chamber 42 for accommodating the rotary valve 41 is formed in the housing of the compressor.
  • the accommodating chamber 42 is extended through the center surrounded with the cylinder bore 11 a in the cylinder block 11 to the center of the rear housing 14 .
  • the valve accommodating chamber 42 has a circular section, and communicated with the suction chamber 28 at its rear end.
  • the valve accommodating chamber 42 and each compression chamber 26 are communicated with each other through each of a plurality of suction communicating passages 43 (see FIG. 3) formed in the cylinder block 11 .
  • the rotary valve 41 is rotatably accommodated in the valve accommodating chamber 42 .
  • the rotary valve 41 is made of an aluminum-series metallic material.
  • the rotary valve 41 has a cylindrical shape.
  • a hole 41 a is bored through the center of a bottom in the forward portion of the rotary valve 41 .
  • the rear end of the drive shaft 16 is placed in the valve accommodating chamber 42 .
  • the drive shaft 16 is fixed to the rotary valve 41 by fitting a small-diameter portion of its rear end into the hole 41 a. Accordingly, the rotary valve 41 and the drive shaft 16 are integrated, and aligned along one axis.
  • the rotary valve 41 is rotated in synchronization with rotation of the drive shaft 16 , i.e., reciprocation of the piston 25 .
  • an internal space of the rotary valve 41 forms an introduction chamber 44 communicated with the suction chamber 28 .
  • a suction guiding groove 45 is formed in a fixed section of a circumferential direction on an outer surface 41 b of the rotary valve 41 .
  • the suction guiding groove 45 and the suction communicating passage 43 constitute a refrigerant gas passage between the introduction chamber 44 as a suction pressure region and the compression chamber 26 .
  • the rotary valve 41 selectively opens/closes the refrigerant gas passage from the suction pressure region to the compression chamber 26 in accordance with relative positions of the suction communicating passage and the suction guiding groove.
  • the front end of the drive shaft 16 is rotatably supported on the front housing 12 through a front bearing 47 composed of a rolling bearing.
  • the rear end of the drive shaft 16 is rotatably supported on the housings 11 , 12 and 14 by direct sliding of the outer surface 41 b of the rotary valve 41 and an inner surface 42 a of the valve accommodating chamber 42 .
  • the rotary valve 41 constitutes a slide bearing surface for supporting the rear end side of the drive shaft 16 by its outer surface 41 b together with the inner surface 42 a of the valve accommodating chamber 42 , and receiving a radial load.
  • a thrust load to the front side of an axis, acted on the drive shaft 16 is received by a thrust bearing 17 between the inner wall surface of the front housing 12 and the lug plate 21 .
  • the bearing 17 is composed of a rolling bearing.
  • a thrust load to the rear side of the axis, acted on the drive shaft 16 is received by sliding of a rear end surface 41 f of the rotary valve 41 on an inner wall surface 14 a of the rear housing 14 .
  • the press-fit position of the rotary valve 41 relative to the drive shaft 16 , or the press-fit distance between the rotary valve 41 and the drive shaft 16 is arranged such that the movable distance of the drive shaft 16 in the axial direction is within 100 ⁇ m.
  • a coating (e.g., later-described coating 48 of FIG. 2) is applied to the rear end surface 41 f of the rotary valve 41 so as to improve sliding characteristics between the rear housing 14 and the rotary valve 41 .
  • this coating may also be applied to the inner wall surface 14 a of the rear housing 14 , or on both of the surfaces 41 f and 14 a.
  • a thrust bearing composed of a rolling bearing may be provided between the rear end surface 41 f of the rotary valve 41 and the inner wall surface 14 a of the rear housing 14 .
  • the inner surface 42 a of the valve accommodating chamber 42 is set to a largest diameter on the assumption that strength of the cylinder block 11 , i.e., predetermined minimum strength of a portion between the valve accommodating chamber 42 and the cylinder bore 11 a, can be maintained.
  • the rotary valve 41 accommodated in the valve accommodating chamber 42 also has a large diameter. In the present embodiment, this diameter is larger than that of the drive shaft 16 .
  • the coating 48 is applied to the entire outer surface 41 b of the rotary valve 41 so as to improve sliding characteristics between the outer surface 41 b and the inner surface 42 a of the valve accommodating chamber 42 .
  • FIG. 2 shows only a part of the coating 48 , which is indicated by a netted portion.
  • the coating 48 is made of, for example a fluorocarbon resin.
  • the fluorocarbon resin includes polytetrafluoroethylene (PTFE), tetrafluoroethylene and perfluoroalkylvinyl ether copolymer (PFA), tetrafluoroethylene and hexafluoropropylene copolymer (FEP), tetrafluoroethylene and ethylene copolymer (ETFE), polyvinylidene fluoride (PVDF), and polychlorotrifluoroethylene (PCTFE).
  • PTFE polytetrafluoroethylene
  • PFA perfluoroalkylvinyl ether copolymer
  • FEP tetrafluoroethylene and hexafluoropropylene copolymer
  • ETFE tetrafluoroethylene and ethylene copolymer
  • PVDF polyvinylidene fluoride
  • PCTFE polychlorotrifluoroethylene
  • a helical pumping groove 49 is formed around an axis of the drive shaft 16 on the outer surface 41 b of the rotary valve 41 .
  • the pumping groove 49 is operated as a pump in cooperation with the inner surface 42 a of the valve accommodating chamber 42 . Therefore, between the outer surface 41 b of the rotary valve 41 and the inner surface 42 a of the valve accommodating chamber 42 , refrigerants present between the peripheral surfaces 41 b and 42 a and lubricating oil contained therein are caused to actively flow.
  • a helical direction of the pumping groove 49 i.e., a flowing direction of the refrigerants and the lubricating oil, may be set in a direction of the crank chamber 15 (left side in the drawing) or in a direction of the suction chamber 28 (right side).
  • the helical direction of the pumping groove 49 is set in the direction of the crank chamber 15 .
  • the first embodiment provides the following advantages.
  • the rotary valve 41 constitutes the slide bearing surface by its outer surface 41 b together with the inner surface 42 a of the valve accommodating chamber 42 .
  • the drive shaft 16 is rotatably supported on the housings 11 , 12 and 14 through the rotary valve 41 . That is, the valve accommodating chamber 42 serves not only to accommodate the rotary valve 41 but also to bear and accommodate the drive shaft 16 .
  • the valve accommodating chamber 42 serves not only to accommodate the rotary valve 41 but also to bear and accommodate the drive shaft 16 .
  • the rotary valve 41 (slide bearing) has a larger diameter than the drive shaft 16 .
  • a surface pressure applied to the outer surface 41 b of the rotary valve 41 can be reduced, and a peripheral velocity of the rotary valve 41 can be increased.
  • oil film cutting between the outer surface 41 b of the rotary valve 41 and the inner surface 42 a of the valve accommodating chamber 42 can be prevented. Therefore, it is possible to improve durability of the slide bearings 41 and 42 .
  • the diameter of the rotary valve 41 When the diameter of the rotary valve 41 is large, the diameter of the inner surface 42 a of the valve accommodating chamber 42 becomes also large. In the cylinder block 11 , a thickness of a portion between the cylinder bore 11 a and the valve accommodating chamber 42 can be reduced. Thus, the suction communicating passage 43 can be as short as possible, and volume efficiency of the compressor can be improved by reducing a dead volume of the compressor chamber 26 .
  • the drive shaft 16 and the rotary valve 41 are provided separately.
  • a shape dimension and a quality of material of the rotary valve 41 are independent of machining and functional restrictions of the drive shaft 16 .
  • the shape dimension and the quality of material of the rotary valve 41 can be selected by giving priority to its functions (including the function of the slide bearing).
  • a straight shape (no outer diameter irregularities) is suitable for improving machining characteristics, and an iron-series metallic material is suitable when durability is taken into consideration.
  • a diameter as large as possible is suitable for improving its durability.
  • a material similar to that of the cylinder block 11 for example, an aluminum-series metallic material, is suitable for preventing enlargement of a clearance between the cylinder block 11 and the rotary valve 41 caused by a difference of a coefficient of thermal expansion from that of the valve accommodating chamber 42 (cylinder block 11 ).
  • the pumping groove 49 is formed on the outer surface 41 b of the rotary valve 41 .
  • refrigerants and/or lubricating oil contained therein are caused to actively flow through the clearance between the outer surface 41 b of the rotary valve 41 and the inner surface 42 a of the valve accommodating chamber 42 by the pumping operation of the pumping groove 49 . Therefore, it is possible to improve sliding characteristics between the outer surface 41 b of the rotary valve 41 and the inner surface 42 a of the valve accommodating chamber 42 .
  • the pumping groove 49 can be easily machined on the outer surface 41 b of the rotary valve 41 .
  • Provision of the helical direction of the pumping groove 49 in the direction of the crank chamber 15 enables lubricating oil to be supplied to the crank chamber 15 .
  • a lubricating state between the swash plate 23 and the shoes 27 can be improved, thereby the durability of the compressor is improved.
  • provision of the helical direction of the pumping groove 49 in the direction to the suction chamber 28 prevents leakage of refrigerant gas from the suction pressure region, i.e., the suction chamber 28 or the introduction chamber 44 , to the crank chamber 15 . Therefore, the compression efficiency of the compressor can be much more increased.
  • a slide bearing surface can be easily formed between the outer surface 41 b of the rotary valve 41 and the inner surface 42 a of the valve accommodating chamber 42 .
  • a supercharging blade 51 which serves as supercharging means is arranged between one surface 45 a and the other surface 45 b of a suction guiding groove 45 of a rotary valve 41 .
  • the supercharging blades 51 are provided in a plurality of places (three places in FIG. 4) to have angles substantially equal to those of the surfaces 45 a and 45 b.
  • the supercharging blade 51 actively supplies the refrigerant gas to a compression chamber 26 .
  • a large amount of refrigerant gas can be sucked into the compressor 26 , thereby increasing further compression efficiency of the compressor.
  • a rotary valve 41 is received by a static pressure in a valve accommodating chamber 42 . That is, a hole 55 is bored through as a pressure supply passage on a wall of the rotary valve 41 .
  • the hole 55 is arranged in a region opposite a suction guiding groove 45 with respect to an axis of a drive shaft 16 .
  • the hole 55 communicates an introduction chamber 44 with a clearance between the rotary valve 41 and the valve accommodating chamber 42 . Accordingly, by application of centrifugal force based on rotation of the rotary valve 41 , refrigerants in the introduction chamber 44 and/or lubricating oil contained therein are supplied through the hole 55 to the clearance between the rotary valve 41 and the valve accommodating chamber 42 . Thus, the rotary valve 41 is received by a static pressure in the valve accommodating chamber 42 .
  • improved sliding characteristics can be provided between an outer surface 41 b of the rotary valve 41 received by the static pressure in the valve accommodating chamber 42 , and an inner surface 42 a of the valve accommodating chamber 42 . Therefore, the outer surface 41 b of the rotary valve 41 and the inner surface 42 a of the valve accommodating chamber 42 can easily constitute a slide bearing surface.
  • the hole 55 is arranged in the region opposite the suction guiding groove 45 with respect to the axis of the drive shaft 16 .
  • the refrigerants and/or lubricating oil contained therein are even supplied through the hole 55 to the region where the clearance is not adjacent to the suction guiding groove 45 , thereby providing good sliding characteristics.
  • This arrangement also facilitates constitution of a slide bearing surface by the outer surface 41 b of the rotary valve 41 and the inner surface 42 a of the valve accommodating chamber 42 .
  • an outer surface 41 b of a rotary valve 41 and an inner surface 42 a of a valve accommodating chamber 42 are tilted in such a direction as to approach an axis of a drive shaft 16 toward the rear side of a compressor, and formed in a taper state. Sliding to the rear side along the axis of the drive shaft 16 is regulated by abutment between the outer surface 41 b of the rotary valve 41 and the inner surface 42 a of the valve accommodating chamber 42 .
  • a slide bearing surface constituted of the outer surface 41 b of the rotary valve 41 and the inner surface 42 a of the valve accommodating chamber 42 receives not only the radial load acted on the drive shaft 16 described above with reference to the first to third embodiments, but also a thrust load acted rearward on the drive shaft 16 .
  • tilt angles of slide bearing surfaces 41 b and 42 a with respect to the axis of the drive shaft 16 are set in a range of greater than 0° to 10° or less, more preferably in a range of 0.5° to 1°.
  • tilt angles of the slide bearing surfaces 41 b and 42 a are shown with exaggeration.
  • the slide bearing surfaces 41 b and 42 a can also receive the thrust load acted on the drive shaft 16 .
  • the bleed passage 36 is provided in the drive shaft 16 and in the front end of the rotary valve 41 in their axial direction.
  • the bleed passage 36 includes a restriction 36 a at its downstream side where the bleed passage 36 connects with the introduction chamber 44 .
  • a refrigerant gas in the crank chamber 15 is introduced into the introduction chamber 44 through the bleed passage 36 and the restriction 36 . Due to the drastically reduced cross-section in the restriction 36 and centrifugal force applied by rotation of the drive shaft 16 , a lubricating oil is separated from refrigerant gas at the upstream side of the restriction 36 a.
  • the front end of the rotary valve 41 has a smaller portion 41 g the diameter of which is smaller than that of the drive shaft 16 .
  • the rotary valve 41 is press-fit through the smaller portion 41 g into the attachment hole 16 b in the rear end of the drive shaft 16 .
  • a oil returning hole 57 is formed through the drive shaft 16 at the overlapping portion of the smaller portion 41 g of the rotary valve 41 and the rear end of the drive shaft 16 .
  • the hole 57 communicates the bleed passage 36 at the upstream side of the restriction 36 a with the crank chamber 15 .
  • the separated oil which is separated from refrigerant gas at the upstream of the restriction 36 a, is returned through the hole 57 to the crank chamber 15 .
  • the fifth embodiment has same advantages as the first embodiment.
  • a lubricating oil which is discharged from crank chamber 15 together with refrigerant gas, may be separated from refrigerant gas in the bleed passage 36 and returned to the crank chamber 15 rapidly.
  • adequate amount of the lubricating oil can be maintained in the crank chamber 15 , causing excellent contact and slidability between the parts in the crank chamber 15 (e.g. between the swash plate 23 and shoes 27 and between the shoes 27 and the piston 25 ).
  • the fourth embodiment (c.f. FIG. 6) may be changed to tapered portions 41 c and 42 b of the outer surface 41 b of the rotary valve 41 and the inner surface 42 a of the valve accommodating chamber 42 .
  • tapering of the rotary valve 41 and the valve accommodating chamber 42 can be facilitated.
  • the tapered portion 41 c of the outer surface 41 b of the rotary valve 41 is provided at the rear of the opening of a suction guiding groove 45 .
  • the tapered portion 42 b of the inner surface 42 a of the valve accommodating chamber 42 is provided at the rear of the opening of a suction communicating passage 43 . That is, the tapered portions 41 c and 42 b are provided away from the opening/closing position of a refrigerant gas passage by the rotary valve 41 .
  • the fourth embodiment (c.f. FIG. 6) may be changed to be curved portions 41 d and 42 c of the outer surface 41 b of the rotary valve 41 and the inner surface 42 a of the valve accommodating chamber 42 in such a direction as to approach the axis of the drive shaft 16 toward the rear side of the compressor.
  • the projected curved portion 41 d of the outer surface 41 b of the rotary valve 41 is provided at the rear of the opening of the suction guiding groove 45 .
  • the recessed curved portion 42 c of the inner surface 42 a of the valve accommodating chamber 42 is provided at the rear of the opening of the suction communicating passage 43 . That is, the curved portions 41 d and 42 c are provided away from the opening/closing position of the passage of refrigerant gas by the rotary valve 41 .
  • the tapered portions of the outer surface 41 b of the rotary valve 41 and the inner surface 42 a of the valve accommodating chamber 42 may be tilted in such a direction as to approach the axis of the drive shaft 16 toward the front side of the compressor.
  • the thrust bearings 17 can be omitted.
  • means e.g., coating
  • the pumping groove 49 may be formed not on the outer surface 41 b of the rotary valve 41 but on the inner surface 42 a of the valve accommodating chamber 42 . Even in such a configuration, an advantage similar to the advantage (5) of the first embodiment can be provided.
  • the pumping groove 49 is not limited to the helical shape.
  • it may be an oblique groove tilted with respect to the axis of the drive shaft 16 .
  • the coating 48 may be formed only on the inner surface 42 a of the valve accommodating chamber 42 .
  • the coating 48 may be formed on both of the outer surface 41 b of the rotary valve 41 and the inner surface 42 a of the valve accommodating chamber 42 .
  • the material for the rotary valve 41 is different from that (aluminum-series metallic material) of the cylinder block 11 .
  • Other metallic materials such as a synthetic resin having a coefficient of thermal expansion close to that of the aluminum-series metallic material, and brass having a coefficient of thermal expansion close to that of the aluminum-series metallic material but not adhered to the same may be used. In such a manner, sliding between the outer surface 41 b of the rotary valve 41 and the inner surface 42 a of the valve accommodating chamber 42 becomes sliding between different materials, thereby eliminating the necessity of the coating 48 .
  • a glass fiber can be suitably used as a reinforcing material.
  • the rotary valve 41 and the cylinder block 11 may be formed of an iron-series metallic material having excellent durability.
  • the rotary valve 41 and the drive shaft 16 may be formed integrally.
  • an advantage similar to the advantage (2) of the first embodiment can be provided.
  • the expression “rotary valve has a larger than drive shaft” includes an arrangement that the rotary valve 41 is formed integrally with the drive shaft 16 , and the portion of the rotary valve 41 has a larger diameter than other portions.
  • the compressor is not limited to the single-head piston type compressor. As shown in FIG. 10, a fixed displacement compressor including a double-head piston may be employed. In the double-head piston type compressor, groups of cylinder bores 11 a are arranged not only on the rear side but also on the front side of the drive shaft 16 . Thus, the rotary valve 41 is applied to the front suction valve mechanism 35 .
  • the front bearing (rolling bearing) 47 is removed, and the rotary valve 41 can be used as a rolling bearing for supporting the front end of the drive shaft 16 . Therefore, it is not necessary to use expensive rolling bearings for all the radial bearings of the drive shaft 16 , making it possible to reduce costs of the compressor further.
  • identical or equivalent members is denoted by similar reference numerals, and description thereof will be omitted.
  • the drive shaft 16 and the rotary valve 41 may not necessarily be separate. As shown in FIG. 10, the drive shaft 16 and the rotary valve 41 may be formed integrally. This reduces the number of the components of the compressor and simplifies the manufacture of the compressor. To form the drive shaft 16 and the rotary valve 41 integrally, machining, casting, forging (e.g. cold forging) may be utilized.
  • FIG. 11 shows an another example of the embodiment of FIG. 10.
  • a drive shaft 16 and a hollow (pipe-like) rotary valve 41 are separate members. These members may be integrate by press-fitting as in the first to fifth embodiments, by welding, or by pressure welding.
  • Pressure welding refers to a method in which, for example in FIG. 11, the smaller portion 16 a of the drive shaft 16 is inserted in the hole 41 a of the rotary valve 41 without play and the drive shaft 16 and the rotary valve 41 are relatively rotated to weld the outer surface of the smaller portion 16 a in the hole 41 a with friction heat.
  • a wave cam may be used.
US10/292,043 2001-11-12 2002-11-12 Piston type compressor Abandoned US20030113211A1 (en)

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JP2001-346625 2001-11-12
JP2001346625 2001-11-12
JP2001377746 2001-12-11
JP2001-377746 2001-12-11
JP2002-325830 2002-11-08
JP2002325830A JP3891099B2 (ja) 2001-11-12 2002-11-08 ピストン式圧縮機

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US20030095876A1 (en) * 2001-11-22 2003-05-22 Tomoji Tarutani Swash plate type compressor
US20050147504A1 (en) * 2003-11-14 2005-07-07 Masaki Ota Variable displacement compressor
US20050196291A1 (en) * 2004-03-03 2005-09-08 Yoshinori Inoue Piston compressor
US20060008359A1 (en) * 2004-07-09 2006-01-12 Masafumi Ito Variable displacement compressor
EP1915531A1 (en) * 2005-08-12 2008-04-30 Halla Climate Control Corporation Compressor
US7458785B2 (en) 2003-02-04 2008-12-02 Kabushiki Kaisha Toyota Jidoshokki Compressor with lubrication structure
US20120251344A1 (en) * 2011-03-31 2012-10-04 Kabushiki Kaisha Toyota Jidoshokki Double-headed piston type swash plate compressor
CN111438743A (zh) * 2020-03-25 2020-07-24 南京工业职业技术学院 一种多用途阵列阀承台切割机
US20210388827A1 (en) * 2020-06-15 2021-12-16 Hanon Systems Vapor injected piston compressor

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CN101503994A (zh) * 2008-02-05 2009-08-12 株式会社丰田自动织机 旋转斜盘式压缩机
JP7048177B2 (ja) * 2018-06-27 2022-04-05 サンデン・オートモーティブコンポーネント株式会社 可変容量圧縮機

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US5626463A (en) * 1992-10-05 1997-05-06 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Axial multi-piston compressor having rotary valve for allowing residual part of compressed fluid to escape
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Publication number Priority date Publication date Assignee Title
US20030095876A1 (en) * 2001-11-22 2003-05-22 Tomoji Tarutani Swash plate type compressor
US7458785B2 (en) 2003-02-04 2008-12-02 Kabushiki Kaisha Toyota Jidoshokki Compressor with lubrication structure
US20050147504A1 (en) * 2003-11-14 2005-07-07 Masaki Ota Variable displacement compressor
US20050196291A1 (en) * 2004-03-03 2005-09-08 Yoshinori Inoue Piston compressor
US7530797B2 (en) 2004-07-09 2009-05-12 Kabushiki Kaisha Toyota Jidoshokki Variable displacement compressor
US20060008359A1 (en) * 2004-07-09 2006-01-12 Masafumi Ito Variable displacement compressor
EP1915531A1 (en) * 2005-08-12 2008-04-30 Halla Climate Control Corporation Compressor
EP1915531A4 (en) * 2005-08-12 2014-03-05 Halla Visteon Climate Control COMPRESSOR
US20120251344A1 (en) * 2011-03-31 2012-10-04 Kabushiki Kaisha Toyota Jidoshokki Double-headed piston type swash plate compressor
US8899943B2 (en) * 2011-03-31 2014-12-02 Kabushiki Kaisha Toyota Jidoshokki Double-headed piston type swash plate compressor
CN111438743A (zh) * 2020-03-25 2020-07-24 南京工业职业技术学院 一种多用途阵列阀承台切割机
US20210388827A1 (en) * 2020-06-15 2021-12-16 Hanon Systems Vapor injected piston compressor
US11629709B2 (en) * 2020-06-15 2023-04-18 Hanon Systems Vapor injected piston compressor

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DE10252447A1 (de) 2003-07-17
CN1419051A (zh) 2003-05-21
JP2003239856A (ja) 2003-08-27
DE10252447B4 (de) 2006-12-21
JP3891099B2 (ja) 2007-03-07

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