EP0175206A1 - Fluid machine - Google Patents

Fluid machine Download PDF

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Publication number
EP0175206A1
EP0175206A1 EP85111087A EP85111087A EP0175206A1 EP 0175206 A1 EP0175206 A1 EP 0175206A1 EP 85111087 A EP85111087 A EP 85111087A EP 85111087 A EP85111087 A EP 85111087A EP 0175206 A1 EP0175206 A1 EP 0175206A1
Authority
EP
European Patent Office
Prior art keywords
float valve
cylinder block
fluid machine
pressure
end plate
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP85111087A
Other languages
German (de)
English (en)
French (fr)
Inventor
Hisanobu Kanamaru
Akira Tohkairin
Kazushi Sasaya
Tomiyasu Onuma
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.)
Hitachi Ltd
Original Assignee
Hitachi Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hitachi Ltd filed Critical Hitachi Ltd
Publication of EP0175206A1 publication Critical patent/EP0175206A1/en
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0044—Component parts, details, e.g. valves, sealings, lubrication
    • F01B3/0055—Valve means, e.g. valve plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0044—Component parts, details, e.g. valves, sealings, lubrication
    • F01B3/0047—Particularities in the contacting area between cylinder barrel and valve plate

Definitions

  • the present invention relates to a fluid machine and, more particularly, to a fluid machine having a valve mechanism which is effective particularly when the fluid machine is used as a compressor or a pump for pressurizing and delivering a fluid such as air, hydraulic oil and so forth.
  • Liquid pumps for pressurizing and delivering a working fluid such as oil and liquid motors for obtaining torque by making use of head energy of working fluid are known as fluid machines.
  • This kind of fluid machine are generally sorted into two types: namely, a rotary swash plate type machine in which, as shown in Fig. 1 attached to Japanese Patent Application Laid-open No. 91383/1983, an oscillation disk on a driven shaft is oscillatorily driven by a swash plate fixed to a drive shaft such that the rotary motion of the drive shaft is changed into a reciprocatory motion, and rotary slant shaft type in which eccentric motion of a slant shaft formed integrally on the output end of a drive shaft is transmitted to an oscillation disk which is mounted through a rotation prevention means on the outer periphery of the slant shaft, thereby converting a rotary motion into reciprocatory motion.
  • a rotary swash plate type machine in which, as shown in Fig. 1 attached to Japanese Patent Application Laid-open No. 91383/1983, an oscillation disk on a driven shaft is oscillatorily driven by a swash plate fixed to a drive shaft such that the rotary motion of the drive shaft
  • the rotary swash plate type machine requires a complicated construction due to necessity of the bearing means such as needle bearing between the swash plate and the oscillation disk for converting the rotary motion of the swash plate into reciprocatory motion of the oscillation disk.
  • the bearing means such as needle bearing between the swash plate and the oscillation disk for converting the rotary motion of the swash plate into reciprocatory motion of the oscillation disk.
  • a large friction resistance is produced in a central ball bearing which supports the oscillation disk and bears all part of the thrust load, resulting in a low mechanical efficiency.
  • the oscillation disk is not allowed to rotate about its axis because the peripheral portion of the oscillation disk carries a plurality of piston rods which in turn are connected to pistons slidably received by respective cylinders.
  • the prevention of rotation of the oscillation disk is achieved through a so-called slide gear type mechanism which employs a meshing engagement between a stationary bevel gear and a spur gear formed on the side surface of the oscillation disk. This mechanism is inherently not durable.
  • the oscillation disk is mounted through a thrust bearing on the outer periphery of the slant shaft which is integral with the drive shaft, so that an axial thrust is generated as in the case of the rotary swash plate type machine.
  • this type of machine also suffers from a problem concerning durability of the mechanism for preventing the rotation of the oscillation disk, as well as the requirement for the thrust bearing to perform various functions, with a result that the construction is too complicated.
  • the long and heavy slant shaft causes an unbalance of rotation mass, resulting in large vibration and noise.
  • the unbalance of rotation mass is encountered also in the rotary swash plate type machine.
  • a balance weight is used for the purpose of eliminating the mass unbalance, vibration cannot be suppressed satisfactorily because it is not allowed to obtain a geometrical balance.
  • the vibration acts as an eccentric load on the drive shaft such as to increase the friction loss of power.
  • the mechanical vibration shortens the life of the machine and impairs the quality of the product as commercial goods because it imparts unpleasant feel to the user.
  • an object of the invention is to provide a fluid machine having a valve mechanism which is simple in construction and high in precision, thereby overcoming the above-described problems of the prior art.
  • a fluid machine in which through bores formed in a cylinder block which is fixed to a rotary shaft are adapted to be closed by float valves which are disposed between the high-pressure chamber and the end surface of the cylinder block and adapted to be pressed onto the end surfaces of the cylinder block by pressure which exists in the high-pressure chamber.
  • the valve mechanism exhibits a high sealing effect because the float valves are pressed against the end surface of the cylinder block at high pressure which is generated in the machine.
  • Fig. 1 is a vertical sectional view of an air compressor which is a first embodiment of the invention, while Figs. 2 and 3 are sectional views taken along the lines II-II and III-III of Fig. 1, respectively.
  • an end plate 3 is attached to open end of a substantially bowl-shaped casing 1 through an "O" ring 2 by means of a plurality of mounting screws 4.
  • a radial bearing 6 mounted on the center of the end plate 3 rotatably carries a rotary shaft 5.
  • a mechanical seal 8 is disposed between the rotary shaft 5 and the inner peripheral wall 3E of the end plate 3 defining the bore receiving the shaft 5, and is prevented from coming off by means of a clip 7.
  • the casing 1 and the end plate 3 are made of aluminum material.
  • the casing 1 accommodates a working chamber assembly 9 and a motion converting mechanism 10.
  • the working chamber assembly 9 is composed of an aluminum cylinder block 12 having a plurality of through bores 11 arranged at a constant circumferential pitch, and pistons 15 received in the through bores 11 and having respective rod portions 13 and ball portions 14.
  • the cylinder block 12 has a central bore into which is pressed and fixed one end of the rotary shaft 5.
  • the fixing of the rotary shaft 5 to the cylinder block 12 may be made by any known mechanical fixing means, as well as press-fit employed in the illustrated embodiment.
  • a reference numeral 16 denotes a thrust bearing arranged coaxially with the rotary shaft 5 and in contact at its one side with the end plate such as to bear the axial thrust load on the rotary shaft 5 and the cylinder block 12.
  • the central bore in the cylinder block 12 is stepped such as to form an enlarged portion 17 which receives, through a buffer spring 19, the drive shaft 18A of a cross-spider type universal joint 18.
  • the end of the drive shaft 18A opposes the end of the rotary shaft 5 through a spacer 20.
  • the drive shaft 18A is secured to the cylinder block 12 by means of a key 21.
  • the universal joint 18 has a driven shaft 22 which is supported, through a radial bearing 24, by the outer periphery of an oblique stationary shaft 23 which is provided on the bottom of the casing 1.
  • a fork-shaped arm 22A integral with the drive shaft 22 is connected through a cross-spider 25 to another fork-shaped arm 18B which in turn is integral with the drive shaft 18A.
  • the inclination of the oblique stationary shaft 23 is attained by forming beforehand a tapered surface on the inner bottom lA of the casing 1 and providing the shaft 23 perpendicularly to the tapered surface.
  • this mechanism has a rotary disk 26 which is fixed at its central portion to the outer periphery of the driven shaft 22 and provided at its peripheral portion with a plurality of ball-receiving recesses which rotatably receive the ball portions 14 of the pistons 15.
  • the motion converting mechanism further has a thrust bearing 27 disposed between the inner bottom surface 1A of the casing 1 and the rear surface of the rotary disk 26 and intended for receiving the load produced by the pistons 15.
  • the end plate is provided in the inner surface 3F thereof with an arcuate low-pressure chamber 3B communicating with a suction port 3A and an arcuate high-pressure chamber 3D which opposes the low-pressure chamber 3B and communicated with a discharge port 3C.
  • a seal ring 28 such as a rubber ring is provided such as to surround the high-pressure chamber 3D thereby defining a high-pressure area 29.
  • This high-pressure area 29 can be formed easily by forming a step in the inner surface of the end plate 3 such that the surface in the high-pressure area 29 is slightly recessed from other portion of the surface, as shown in sectional view in Fig.
  • the float valve 30 constituting the cylinder head is composed of a dough-nut shaped iron plate which is disposed between the end plate 3 and the cylinder block 12 concentrically with the latter. As shown in Fig. 2, the float valve is provided with a high-pressure passage 30A and a low-pressure passage 30B which are arranged to oppose the chambers 3B and 3D formed in the end plate 3. A small annular gap is formed between the outer peripheral surface of the float valve 30 and the inner peripheral surface of the casing 1.
  • the float valve itself is located substantially in the high-pressure side, so that the arrangement may be such that an iron sheet is cut out in an arcuate form in a size slightly greater than the size of the seal ring 2, while other iron plate is fixed to the casing 1.
  • the cylinder block 12 is rotated in synchronism with the rotary shaft 5, followed by rotation of the driving side, cross-spider 25 and the driven side of the universal joint 18. Consequently the rotary disk 26 is rotated simultaneously.
  • the invention does not exclude a modification in which the float valve is provided only at the high-pressure side.
  • the cylinder head can be formed from a material different from the material of the cylinder head. This is quite advantageous from the view point of reduction in the weight of the machine.
  • Fig. 4 shows another modification which is distinguished from the embodiment shown in Fig. 1 in that a bevel gear is used in place of the universal joint shown in Fig. 1. More specifically, in this modification, a tubular member 40 is fixed by press fit to the end of the rotary shaft 5. The tubular member 40 is press-fitted in the cylinder block 12 and is provided at its end with a bevel gear 40A. The tubular member 40 receives a ball holder 42 which is urged by a buffer spring 41 also received by the tubular member 40. A tubular member 43 is provided with a bevel gear 43A meshing with the bevel gear 40A and a ball holder 44. The ball holders 42 and 44 are provided in the center thereof with spherical recesses which receive a common ball 45.
  • the ball holders are made of an aluminum-silicon alloy.
  • the driving coupling is achieved by means of bevel gears such that the pistons 15 are reciprocatingly driven in accordance with the rotation of the rotary disk 26.
  • Other portions of the mechanical construction and the operation are the same as those in the embodiment described before, so that detailed description thereof is omitted in this specification.
  • Figs. 5 and 6 show a hydraulic pump which is another embodiment of the fluid machine in accordance with the invention.
  • the basic construction of this embodiment is materially identical to that of the first embodiment shown in Fig. 1, except the construction of the float valve mechanism. The following description, therefore, will be concentrated to the float valve mechanism.
  • a stepped groove 53 is formed around the high-pressure passage 52 formed in the end plate 50 in communication with the discharge port 51.
  • the bottom surface of the stepped groove 53 is greater than the width of cross-section of the seal ring 54 for example.
  • the float valve 55 contacting the cylinder block 12 has an arcuate form with a convexed cross-sectional shape such as to fit in the stepped groove 53.
  • the width of the end of cross-section of the float chamber 55 is determined to be greater than the width of section of the seal ring 54.
  • a high-pressure area is formed on the end of the float valve.
  • the float valve 55 is pressed towards the cylinder block 12 such as to form a tight seal between itself and the cylinder block 12.
  • a thrust plate 56 is positioned such as to oppose the float valve 55.
  • This thrust place 56 intended for attaining a balanced rotation of the cylinder block 12, is provided in the surface thereof with a channel 57 and is fixed to the front cover 50 by means of fixing screws 58.
  • the described constructions of the float valve are only illustrative and can have various other forms because the self-closing nature of the float valve can be attained by suitably selecting the area ratio.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
EP85111087A 1984-09-05 1985-09-03 Fluid machine Withdrawn EP0175206A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP184648/84 1984-09-05
JP59184648A JPS6165081A (ja) 1984-09-05 1984-09-05 流体機械

Publications (1)

Publication Number Publication Date
EP0175206A1 true EP0175206A1 (en) 1986-03-26

Family

ID=16156907

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85111087A Withdrawn EP0175206A1 (en) 1984-09-05 1985-09-03 Fluid machine

Country Status (3)

Country Link
EP (1) EP0175206A1 (ja)
JP (1) JPS6165081A (ja)
AU (1) AU4699685A (ja)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5247794A (en) * 1990-09-11 1993-09-28 Sundstrand Corporation Cylinder block positive hold-down for cold start-up
EP0608144A2 (en) * 1993-01-21 1994-07-27 David Brown Hydraulics Limited Axial piston pump
WO2002035094A1 (en) * 2000-10-28 2002-05-02 Airzen Co., Ltd. Rotary slant shaft type gas compressor with multi-stepped exhaust system
EP1279830A1 (en) * 2001-07-27 2003-01-29 Teleflex Canada Limited Partnership Swash plate pump
DE102017105610A1 (de) * 2017-03-16 2018-09-20 Volkswagen Aktiengesellschaft Axialkolbenmotor und Kreisprozessvorrichtung
CN112983772A (zh) * 2021-03-30 2021-06-18 中航力源液压股份有限公司 一种降低滑履磨损的轴向柱塞泵回程装置

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5175563A (en) * 1986-02-03 1992-12-29 Canon Kabushiki Kaisha Image recording apparatus and ink sheet cassette usable in the image recording apparatus
JPS6331268U (ja) * 1986-08-12 1988-02-29
KR20010016078A (ko) * 2000-10-28 2001-03-05 정규옥 다단 배기시스템을 구비한 사축식 압축장치

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3124079A (en) * 1964-03-10 Jxanjacquxs j joyer
DE1810778A1 (de) * 1968-11-25 1970-07-30 Hashemi Hadi Tafreshi Maschine zum Energieaustausch zwischen Hoch- und Niederdrucksystemen
US3910587A (en) * 1974-08-02 1975-10-07 Universal Eng Face seal structure

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3124079A (en) * 1964-03-10 Jxanjacquxs j joyer
DE1810778A1 (de) * 1968-11-25 1970-07-30 Hashemi Hadi Tafreshi Maschine zum Energieaustausch zwischen Hoch- und Niederdrucksystemen
US3910587A (en) * 1974-08-02 1975-10-07 Universal Eng Face seal structure

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5247794A (en) * 1990-09-11 1993-09-28 Sundstrand Corporation Cylinder block positive hold-down for cold start-up
EP0608144A2 (en) * 1993-01-21 1994-07-27 David Brown Hydraulics Limited Axial piston pump
EP0608144A3 (en) * 1993-01-21 1994-12-21 Hamworthy Hydraulics Ltd Axial piston pump.
WO2002035094A1 (en) * 2000-10-28 2002-05-02 Airzen Co., Ltd. Rotary slant shaft type gas compressor with multi-stepped exhaust system
US6669450B2 (en) * 2000-10-28 2003-12-30 Airzen Co., Ltd. Rotary slant shaft type gas compressor with multi-stepped exhaust system
EP1279830A1 (en) * 2001-07-27 2003-01-29 Teleflex Canada Limited Partnership Swash plate pump
US6579072B2 (en) 2001-07-27 2003-06-17 Teleflex Canada Limited Partnership Swash plate pump with low stress housing
DE102017105610A1 (de) * 2017-03-16 2018-09-20 Volkswagen Aktiengesellschaft Axialkolbenmotor und Kreisprozessvorrichtung
CN112983772A (zh) * 2021-03-30 2021-06-18 中航力源液压股份有限公司 一种降低滑履磨损的轴向柱塞泵回程装置
CN112983772B (zh) * 2021-03-30 2022-08-19 中航力源液压股份有限公司 一种降低滑履磨损的轴向柱塞泵回程装置

Also Published As

Publication number Publication date
AU4699685A (en) 1986-03-13
JPS6165081A (ja) 1986-04-03

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Inventor name: KANAMARU, HISANOBU

Inventor name: TOHKAIRIN, AKIRA

Inventor name: SASAYA, KAZUSHI

Inventor name: ONUMA, TOMIYASU