WO2001071188A1 - Machine a deplacement alternatif - Google Patents

Machine a deplacement alternatif Download PDF

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Publication number
WO2001071188A1
WO2001071188A1 PCT/JP2000/001649 JP0001649W WO0171188A1 WO 2001071188 A1 WO2001071188 A1 WO 2001071188A1 JP 0001649 W JP0001649 W JP 0001649W WO 0171188 A1 WO0171188 A1 WO 0171188A1
Authority
WO
WIPO (PCT)
Prior art keywords
reciprocating
piston
revolving
working chamber
fixed
Prior art date
Application number
PCT/JP2000/001649
Other languages
English (en)
Japanese (ja)
Inventor
Isao Hayase
Kunihiko Takao
Takeshi Tsuchiya
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.
Priority to PCT/JP2000/001649 priority Critical patent/WO2001071188A1/fr
Publication of WO2001071188A1 publication Critical patent/WO2001071188A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B25/00—Multi-stage pumps
    • 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
    • F04B39/0094—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 crankshaft

Definitions

  • the present invention relates to a positive displacement machine, and more particularly to a positive displacement compressor suitable for use in a refrigerating cycle such as a refrigerator and an air conditioner, and an air compressor.
  • the drive torque fluctuates greatly because a single piston repeatedly alternates between suction, compression and discharge, and unbalance due to the reciprocating motion of the piston.
  • the inertia force s was generated, causing the compressor to increase the excitation force.
  • the compression mechanism and the drive motor must be floated in a sealed container with a panel, which causes the compressor to become larger and increase the cost. Had become.
  • a single relatively large piston is required to replace all required replacement sheets (Rule 26).
  • a large differential pressure s which reaches the difference between the compressor suction pressure and the compressor discharge pressure, acts on the seal between the reciprocating biston and the cylinder pore, increasing the internal leakage of working gas and increasing the compressor pressure. Was causing a decrease in efficiency.
  • the residual gas volume at the top dead center position of the biston increases due to the suction valve attached to the cylinder head, which causes the compressor performance to decrease due to the re-expansion of the residual gas.
  • the working gas is sucked into the working chamber via the suction valve, and the passage resistance is large. Had become.
  • An object of the present invention is to improve the technical problems of the prior art described above and to provide a positive displacement compressor in which both torque fluctuation and unbalanced inertial force, which are factors of the exciting force, are small and low in vibration. is there.
  • the above object is a displacement type displacement paper provided with a reciprocating member that is connected to a drive shaft and reciprocates with the rotation of the drive shaft, and the reciprocation causes a change in volume in the working chamber (Rule 26). This is achieved by providing a reciprocating translation member connected to the drive shaft and reciprocating with the rotation of the drive shaft.
  • the above object is to provide a capacity machine having a reciprocating member connected to a drive shaft and reciprocating with the rotation of the drive shaft, and a volume change occurs in the working chamber due to the reciprocation.
  • This is achieved by providing a reciprocating balance member that is connected and reciprocates with the rotation of the drive and shaft, and a balance weight provided on the drive shaft and based on the reciprocating member and the reciprocal balance member.
  • the above object is to provide a cylindrical orbiting member that performs a revolving motion, a drive mechanism that provides the orbital motion to the orbiting member, a fixed frame member that supports the driving mechanism, and a reciprocating motion of the orbiting member. And is supported so as to be able to reciprocate in a direction substantially perpendicular to the axis of the bore, and is operated by reciprocating relative to the revolving member or reciprocating relative to the fixed frame member.
  • the object is to provide a revolving piston having a revolving motion, a crank pin portion rotatably inserted into the revolving piston, a crankshaft for revolving the revolving piston, and supporting the crankshaft.
  • a fixed frame member a movable cylinder having at least one fixing piece Sutonboa protruding orthogonally to the swivel Bisutonka s orbiting piston bore portion inserted reciprocally and the orbiting piston bore, each fixed Pisutonpoa
  • At least one fixed piston inserted in a reciprocating motion and fixed to the fixed frame member, and at least one end face of the revolving piston bore portion is closed and replaced paper (Rule 26)
  • At least one cylinder head fixed to the fixed frame member; and at least one cylinder head formed by the head end face of each of the turning pistons, the orbiting piston bore portion, and each of the cylinder heads.
  • a second working chamber formed by at least one working chamber, at least one fixed bisdon pore portion, a respective fixed piston, and an outer periphery of the orbiting piston, and the second working chamber with the revolving motion of the orbiting piston.
  • a fluid inflow / outflow mechanism for compressing the fluid by increasing or decreasing the volumes of the first working chamber and the second working chamber; and a second reciprocating member reciprocating in a direction substantially perpendicular to the movable cylinder.
  • FIG. 1 is a side sectional view showing a positive displacement compressor according to a first embodiment of the present invention
  • FIG. 2 is a sectional view taken along line II of FIG. 1
  • FIG. FIG. 4 is a cross-sectional view of FIG. 1
  • FIG. 4 is a view showing the movement of each part when the drive shaft of the configuration of FIG. 2 is rotated by 90 °
  • FIG. 6 is a side sectional view showing a positive displacement compressor according to a second embodiment of the present invention
  • FIG. 6 is a sectional view taken along the line III-III of FIG. Best mode for carrying out the invention
  • FIGS. 1 and 2 A first embodiment of the present invention will be described with reference to FIGS.
  • a driving mechanism including a revolving piston 1 for revolving motion, a crankshaft 2 for revolving the revolving biston 1 and a driving motor 8, and a fixed support for the driving mechanism
  • a movable cylinder 4 having a frame member 3, a revolving piston pore portion 4 a for reciprocatingly inserting the revolving piston 1, and at least one fixed piston bore portion 4 c projecting orthogonally to the revolving biston bore portion 4 a; At least one of the fixed pistons 5 inserted into the fixed piston bore portion 4c so as to be able to reciprocate and fixed to the fixed frame member 3, and at least one of the end faces of the revolving piston stone portion 4a is closed to fix the fixed frame member.
  • At least one first working chamber 12 is formed by the cylinder head 6, and the outer peripheral cylindrical surface 1 a of each swivel screw-in 1, the respective fixed screw-ton bore 4 c, and the respective fixed piston 5 to form at least one second working chamber 13, and increase or decrease the volume of each of the first working chambers 12 and each of the second working chambers 13 along with the revolving motion of the orbiting piston 1.
  • a fluid inflow / outflow mechanism including a suction port and a discharge port for a fluid to be transferred or compressed is provided.
  • a reciprocating member 26 through a slider 25 through a tip end of a crankpin portion 2a is provided. Is reciprocated in the direction perpendicular to the movable cylinder 4.
  • the revolving piston 1 has an outer peripheral cylindrical surface portion 1a and a central cylindrical hole portion 1b orthogonal to the outer cylindrical surface portion 1a.
  • the crank pin portion 2a of the crank shaft 2 is rotatably inserted into the cylindrical hole portion 1b, and imparts revolving motion to the revolving piston 1.
  • the crankshaft 2 is rotatably supported by a bearing 3 a of a fixed frame 3.
  • the outer peripheral cylindrical surface portion 1a of the revolving piston 1 is inserted into the revolving piston bore portion 4a formed in the movable cylinder 4 in a reciprocating motion force s : I dog state.
  • the crank pin portion 2a is inserted into the cylindrical hole portion 1b of the revolving piston 1 through the elongated hole portion 4b formed in the movable cylinder 4.
  • the movable cylinder 4 also has fixed piston pores 4c having smaller inner diameters formed on both sides of the swivel piston 'tonbore 4a, and each of the movable pistons 4 is orthogonally connected to the swivel piston pore 4a.
  • the two fixed piston bores 4 c have two fixed pistons 5 each. Replacement paper (Rule 26) These cylindrical outer peripheral surface portions 5 a are inserted from both sides in a state where relative reciprocating motion is possible, and each fixed piston 5 is fixed to the fixed frame 3.
  • the fixed frame 3 is also fixed so that the two cylinder heads 6 force s respectively close the openings at both ends of the orbiting piston bores 4 a of the movable cylinder 4.
  • the cylinder head 6 and the end of the revolving piston bore 4a are not fixed to each other, but have a small gap so that relative movement between the rainy people is possible.
  • the direction of the plane part 6a of the cylinder head 6 is perpendicular to the center axis of the revolving piston bore part 4a and parallel to the center axis of the fixed piston bore part 4c.
  • the seal member 7 is incorporated for airtightness of the minute gap.
  • the slider 25 has a rectangular parallelepiped shape, and has two parallel flat portions 25a and a central cylindrical hole portion 25b orthogonal to the flat portion 25a.
  • the central cylindrical hole 25b is rotatably inserted into the tip of the crankpin 2a.
  • the flat portion 25a is also inserted so as to be capable of a relative reciprocating motion to two parallel flat portions 26a of the reciprocating member 26, and the reciprocating member 26 is a rod portion thereof.
  • 2 6b is guided by the reciprocating motion guide portion 6d of the cylinder head 6 integrally fixed to the fixed frame 3, so that a reciprocating motion force 5 in a direction perpendicular to the reciprocating direction of the movable cylinder 4 is provided. 'Possibly supported.
  • the rotor 8a of the drive motor 8 is mounted on the crankshaft 2, and the stator 8b of the drive motor 8 is fixed to the main chamber 9 together with the fixed frame 3. I have. Openings at both ends of the main chamber 9 are closed by the upper chamber 10 and the lower chamber 11 to form a closed container.
  • the above-mentioned configuration allows the crank replacement sheet (Rule 26).
  • the orbiting piston 1 revolves due to the eccentric motion of the crank pin portion 2a.
  • the movement of the swiveling piston 1 in the direction of the piston piston 4 a was not transmitted to the movable cylinder 4 because the rainy person could slide on each other in that direction, and was guided to the movable cylinder 4 by the fixed piston 5.
  • Fixed piston bore 4 Only reciprocating motion in C direction is transmitted. At this time, the swivel piston 1 reciprocates in the swivel piston pore 4a.
  • the head end face 1 c of the orbiting piston turning Bisutonpoa portion 4 a and cylindrical Dae' de of the flat portion 6 a and two first-stage working chamber being formed with a relatively large maximum volume by the sealing member 7 (First working chamber) 1 2, formed by outer cylindrical surface 1 a of swivel piston 1, fixed piston bore 4 c and fixed piston head 5 b, each having a relatively small maximum volume 2
  • First working chamber formed by outer cylindrical surface 1 a of swivel piston 1, fixed piston bore 4 c and fixed piston head 5 b, each having a relatively small maximum volume 2
  • Four second-stage working chambers (second working chambers) 13 a total of four working chambers, repeatedly increase and decrease in volume as the crankshaft 2 rotates.
  • the slider 25 also revolves due to the eccentric motion of the crank pin portion 2a, but the movement of the slider 25 in the plane portion 26a direction is the same in both directions.
  • the working gas (fluid) at the suction pressure is compressed from the suction port 15 of the two places where the suction pipe 14 after branching into two is connected to the main chamber 9
  • the air flows into the machine, passes through the first-stage suction port (first suction port) 6 b formed in the cylinder head 6, and is sucked into the first-stage working chamber 12.
  • the movable cylinder 4 is guided by the fixed piston 5 and reciprocates in the direction of the piston bore 4c, the flat portion 6a of the cylinder head 6 increases the volume of the first-stage working chamber in the suction stroke. Only in the case of, there is a portion exposed to the first-stage working chamber 12.
  • the suction port 6b is a flat sheet for cylinder head 6 (Rule 26) Formed in such a portion of the surface portion 6a, even if the suction valve is not mounted, the working gas once sucked flows through the suction port 6b during the compression stroke in which the volume of the working chamber 12 decreases. There is no backflow.
  • the working gas compressed to the intermediate pressure in the first-stage working chamber 12 is supplied to the first-stage discharge port 6c formed in the cylinder head 6 and the discharge valve mounted on the cylinder head 6. After passing through the preload spring 17 and the valve support member 18, the fluid is discharged into a space 19 in a closed container formed by the main chamber 9, the upper chamber 10 and the lower chamber 11. Since the revolving piston 1 reciprocates in the direction of the piston bore 4 a of the movable cylinder 4, the suction stroke in which the volume of the second-stage working chamber 13 increases also on the surface of the outer cylindrical surface 1 a of the revolving piston.
  • a second-stage suction port (second suction port) Id is formed in such a portion on the outer peripheral cylindrical surface 1a of the orbiting piston.
  • the specific shape of the suction port 1d is a groove formed on the outer circumference of the revolving piston 1 so as to reach the elongated hole 4b opening in the revolving piston bore 4a of the movable cylinder 4 '. It is a passage with a shape, and communicates the space 19 in the closed container with the working chamber 13 only when the working chamber 1'3 is in the suction stroke. Therefore, even if the suction valve is not mounted, the working gas once sucked does not flow back to the space 19 in the closed container during the compression stroke.
  • the working gas at the intermediate pressure in the space 19 passes through the suction port 1 d from the space 19 in the closed container, is further compressed after being sucked into the respective working chambers 13, and is further compressed.
  • the discharge pipe 23 flows out of the compressor at discharge pressure from discharge ports 24 at two places.
  • the relationship between the conventional piston head and the bore of the cylinder that guides the reciprocating motion is reversed, and instead of the outer cylindrical surface of the piston, the inner cylindrical surface is replaced (Rule 26). It is formed as a fixed piston pore portion 4c of the movable cylinder, and the cylinder has an evening cylindrical surface instead of the inner cylindrical surface of the pore to form a fixed piston head 5b.
  • the compression work per working chamber is reduced, and further, since the phases thereof are shifted from each other, the overall driving torque fluctuation is reduced. It is done. Furthermore, because of the two-stage compression system, the pressure ratio in each working chamber is reduced, which also reduces the drive torque fluctuation itself in each working chamber. As a result, torque fluctuations are greatly uniformed
  • a second reciprocating member (26) that makes a reciprocating motion in a direction substantially perpendicular to the movable cylinder (4) as the first reciprocating member is provided.
  • the resultant force of the respective reciprocating inertial forces can be made a load having a substantially constant magnitude and rotating in the direction substantially at the rotation speed of the crankshaft 2. This load is equivalent to the centrifugal force acting on the eccentric mass, and can be balanced by the counterweight fixed to the crankshaft 2.
  • the combined force of inertia force is a load that rotates at the rotational speed of the crankshaft 2 with a constant magnitude, and the counterweight fixed to the crankshaft 2. It is understood that 2 b can be balanced. From the above formula, for example, a so-called single-cylinder reciprocating machine having only one piston that reciprocates in a cylinder by a drive shaft known as a refrigerator compressor is driven by a drive shaft that drives the piston.
  • each working chamber only needs to consume a part of the work, so that each working cold is miniaturized, and it is arranged radially around the rotation axis of the driving motor. The whole compressor is reduced in diameter, instead of protruding largely in the radial direction.
  • the mass of the movable cylinder 4 is reciprocated by the reciprocating member, and the mass of 26 is multiplied by 2 with the equations (6) and (7), differentiated twice with time t, and further multiplied by (-1).
  • the inertial forces F x , F y in the reciprocating direction of are expressed by the following equations.
  • the maximum attained pressure is an intermediate pressure, so that the head 1C of the revolving piston is located at the head 1C.
  • Applied compressive load s' small.
  • Razz I contracture in maximum ultimate pressure reaches the discharge pressure, the compression acting on the fixed piston Tonboa ⁇ Ka? Relatively small because the turning Bisuton outer peripheral cylindrical surface portion 1 a The load is small.
  • the suction valve since the suction valve is not required, the passage resistance of the suction passage and the residual gas space in the working chamber can be reduced, and the efficiency and capacity of the compressor are improved. There is.
  • the pressure ratio of each stage is significantly reduced due to the two-stage compression, the adverse effect of the re-expansion of the residual gas in each working chamber is reduced, and the performance of the compressor is improved. This has the effect.
  • the space 19 in the sealed container has an intermediate pressure, and in order to maintain the airtightness of the first-stage working chamber 12, at most the intermediate pressure and the suction pressure are required. Only the differential pressure needs to be sealed, and the airtightness of the second-stage working chamber 13 is maintained. In order to maintain the pressure, only the differential pressure between the discharge pressure and the intermediate pressure needs to be sealed. In other words, the differential pressure to be reduced is smaller than the differential pressure between the discharge pressure and the suction pressure in the case of the conventional single-stage compression, and this has the effect of improving the efficiency and capacity of the compressor by reducing internal leakage. .
  • FIGS. 5 and 6 show a second embodiment of the present invention. Since the basic structure is similar to that of the first embodiment shown in FIGS. 1 to 4, it will be described mainly on the parts unique to the second embodiment.
  • the reciprocating piston member 27 is fixed to the lower part of the crankshaft 2 ′ via a condro 29 connected by a biston pin 28 ′.
  • the reciprocating member 26 ′ reciprocates in the same direction and in substantially the same phase by the second crankpin member 30 thus formed.
  • the sum of the mass of the reciprocating piston member 27, the mass of the piston pin 28, and a part of the mass of the connecting rod 29 (the mass around the small end) is provided as the third reciprocating mass,
  • the inertial force F x in the X-axis direction is expressed by the following equation (8).
  • inertial force F y + F y inertia mosquito ⁇ and y-axis direction of the X-axis direction is vector synthesized as a force acting in the axial direction of the same plane, the size Is constant and the load rotates at the rotation speed of the crankshaft 2 '.
  • the inertia balance can be more completely achieved in the second embodiment, so that there is an effect that a positive displacement compressor with lower vibration can be provided as compared with the first embodiment.
  • the other effects of the first embodiment can be similarly obtained in the second embodiment.
  • the third reciprocating mass in the second embodiment is the second crank pin.
  • the member 30, the connector 29, the piston pin 28, the reciprocating piston member 27, and the reciprocating piston member 2 The reciprocating motion is given by a “crank-slider mechanism” consisting of a cylinder member 32 that guides the reciprocating motion of the reciprocating motion.
  • a reciprocating motion may be provided using the "Scotch yoke mechanism” that provides motion.
  • the reciprocating motion is given to the second reciprocating mass by the “sketch choke mechanism”, but the reciprocating motion is given to the “crank-slider mechanism”. Even if the structure is changed, the effects of the invention described above can be obtained almost in the same manner. ,
  • two first working chambers and two working chambers are respectively provided inside the swivel piston bore of the movable cylinder and inside the fixed piston bore.
  • a total of two working chambers can be formed.
  • Ki they force Turning to repeat the offset change in the volume of the bis tons revolving nine 0 ° with the motion transfer, de be be made by dispersing the four overall workload in each working chamber, In addition to the reduction of the driving torque fluctuation of each working chamber, the driving torque fluctuations having a phase shift are superimposed and the torque fluctuation force s is made uniform.
  • the first working chamber and the second working chamber are sealed spaces formed by inner peripheral wall surfaces that are constituted by both ends or the outer periphery of the swivel piston, and the pressure of each working chamber is directly applied to both ends of the swivel piston. And the outer periphery, and then the turning piston is directly supported by the sliding load of the crankpin of the crankshaft.
  • the conventional technology causes a large sliding load to act and increases the friction loss.
  • the number of sliding portions corresponding to the sliding portion between the slider and the piston, which has been reduced, is reduced, and the efficiency of the compressor can be improved.
  • crankshaft always performs effective compression work for the other working chamber even if it does not perform compression work for one working chamber at the top dead center, and friction due to bearing load Losses always occur for a certain amount of useful work, and the ratio of friction loss to useful work can be reduced and efficiency can be improved.
  • the movable cylinder When each working chamber changes its volume, the movable cylinder reciprocates with respect to the cylinder head, and the orbiting piston reciprocates with respect to the movable cylinder.
  • the cylinder head forming the first working chamber in the swiveling piston port of the movable cylinder and the side of the swiveling piston forming the second working chamber in the fixed piston bore have the respective working chamber volumes. It is possible to open the suction port exposed to the working chamber only while the pressure increases, eliminating the need for the suction valve that caused the increase in the passage resistance.
  • a residual gas space is created in a part other than the lift restriction part of the suction valve and the part on the cylinder head surface where the suction valve is mounted, whereas there is no suction valve.
  • the structure enables a design to reduce the residual gas volume.
  • the differential pressure to be sealed in the first working chamber of the first stage is the differential pressure between the suction pressure of the compressor and the intermediate pressure
  • the second pressure of the second stage is The differential pressure to be sealed in the working chamber.
  • both are smaller than the differential pressure between the suction pressure and the discharge pressure, which is the conventional differential pressure to be sealed. Leakage is reduced.
  • the pressure ratio in each stage is smaller than the pressure ratio when compression is completed in one stage, so the influence of the re-expansion of residual gas in each working chamber s can be reduced, and the capacity of the compressor can be improved.
  • the component configuration of the compressor and the shape and function of each component are not much different from those of the components of the conventional reciprocating compressor, and conventional equipment and processing for efficient cylindrical and planar processing are efficient. Since technology can be used, low-cost production is possible.

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

Abstract

Machine à déplacement alternatif dans laquelle une deuxième masse (26) effectuant un déplacement alternatif à angle droit par rapport au déplacement alternatif d'une première masse (A) est ajoutée à ladite première masse (A) afin de créer un mécanisme de compression. La force résultant des forces d'inertie du déplacement alternatif est convertie en une charge dont le niveau est constant et qui est entraînée par un arbre d'entraînement (2), de manière à maintenir un équilibre avec une force centrifuge d'une masse excentrique (2b) fixée à cet arbre d'entraînement. On ajoute également une troisième masse (27) effectuant un déplacement alternatif dans le même sens que la deuxième masse (26) dans une autre position dans un sens axial, de façon à conserver un équilibre avec un couple, ce qui permet, étant donné que le mécanisme de compression possède des cylindres multiples et, de plus, limite toute variation du couple d'entraînement en tant que mécanisme approprié à une compression à deux étages, de limiter le déséquilibre provoqué par la force d'inertie afin de diminuer les vibrations.
PCT/JP2000/001649 2000-03-17 2000-03-17 Machine a deplacement alternatif WO2001071188A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/JP2000/001649 WO2001071188A1 (fr) 2000-03-17 2000-03-17 Machine a deplacement alternatif

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2000/001649 WO2001071188A1 (fr) 2000-03-17 2000-03-17 Machine a deplacement alternatif

Publications (1)

Publication Number Publication Date
WO2001071188A1 true WO2001071188A1 (fr) 2001-09-27

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2000/001649 WO2001071188A1 (fr) 2000-03-17 2000-03-17 Machine a deplacement alternatif

Country Status (1)

Country Link
WO (1) WO2001071188A1 (fr)

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