EP1342920A2 - Ausgleichsystem für verdichter - Google Patents

Ausgleichsystem für verdichter Download PDF

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Publication number
EP1342920A2
EP1342920A2 EP03005001A EP03005001A EP1342920A2 EP 1342920 A2 EP1342920 A2 EP 1342920A2 EP 03005001 A EP03005001 A EP 03005001A EP 03005001 A EP03005001 A EP 03005001A EP 1342920 A2 EP1342920 A2 EP 1342920A2
Authority
EP
European Patent Office
Prior art keywords
drive shaft
central axis
mass
rotational
mass bodies
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Withdrawn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
EP03005001A
Other languages
English (en)
French (fr)
Other versions
EP1342920A3 (de
Inventor
Masaki Ota
Takeshi Kawata
Takahiro Suzuki
Akinobu Kanai
Taku Adaniya
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.)
Toyota Industries Corp
Original Assignee
Toyota Industries Corp
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 Toyota Industries Corp filed Critical Toyota Industries Corp
Publication of EP1342920A2 publication Critical patent/EP1342920A2/de
Publication of EP1342920A3 publication Critical patent/EP1342920A3/de
Withdrawn legal-status Critical Current

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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
    • 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
    • F04B39/0027—Pulsation and noise damping 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
    • F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
    • F04B27/0895—Component parts, e.g. sealings; Manufacturing or assembly thereof driving 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
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication

Definitions

  • the present invention relates to a compressor provided with a conversion mechanism to convert rotational motion of a drive shaft into compression motion of a compression member in a compression mechanism.
  • the hinge mechanism is provided at a top dead center portion around the axis of the drive shaft. Accordingly, the conversion mechanism is structured so as to have offset load around the axis of the drive shaft. The offset load may be a factor to generate vibration during rotation of the drive shaft.
  • a counter weight is attached to a bottom dead center portion around the axis of the drive shaft in the swash plate.
  • the counter weight is capable of canceling the offset load of the conversion mechanism.
  • the counter weight is provided at the bottom dead center portion of the rotor to fix mass balance around the axis of the drive shaft, for example.
  • the counter weight as large or much mass as possible to deal with the offset load needs to be provided, which is a factor to cause the compressor to be large or heavy.
  • the present invention is directed to a compressor that is capable of reducing the rotational vibration or vibration caused by the offset load around the axis of a drive shaft of a conversion mechanism and that can be small and lightweight.
  • a compressor includes a drive shaft, a conversion mechanism, a rotation body and a mass body.
  • the conversion mechanism converts rotational motion of the drive shaft into compression motion of a compression member in a compression mechanism.
  • the rotation body is provided with the drive shaft so as to integrally rotate with the drive shaft.
  • the drive shaft and the rotation body have a rotational central axis.
  • the mass body is provided with the rotation body.
  • the mass body performs pendulum motion whose center is an axis that is remote from the rotational central axis by a predetermined distance and that is substantially parallel with the rotational central axis.
  • the compressor is characterized in that the mass body is provided to cancel offset load of the conversion mechanism around the rotational central axis of the drive shaft.
  • FIG. 1 A first preferred embodiment of the present invention will now be described with reference to Figs. 1, 2A and 2B. Note that the left side and the right side of Fig. 1 are the front and the rear of the compressor in Fig. 1, respectively.
  • a compressor C includes a cylinder block 11, a front housing 12 joined and fixed to the front end thereof, and a rear housing 14 joined and fixed to the rear end of the cylinder block 11 via a valve plate assembly 13.
  • the cylinder block 11, the front housing 12, the valve plate assembly 13, and the rear housing 14 constitute the housing of the compressor C.
  • a crank chamber 15 is defined in a region surrounded by the cylinder block 11 and the front housing 12.
  • a drive shaft 16, which is provided so as to penetrate the crank chamber 15, is rotatably supported in the housing.
  • the front end of the drive shaft 16 is arranged so as to penetrate a front wall of the front housing 12 and protrude outside.
  • the front end of the drive shaft 16 is connected for operation to a vehicle engine E as an external drive source via a pulley 17 as a rotation body (described later) and a belt 18 partially wound around the pulley 17.
  • a lug plate 19 is fixed to the drive shaft 16 so as to integrally rotate with the drive shaft 16 in the crank chamber 15. Thereby, the lug plate 19 has the same rotational central axis as the drive shaft 16.
  • a swash plate 20 as a cam plate is housed in the crank chamber 15. The swash plate 20 is supported so as to be capable of sliding and inclining with respect to an axis of the drive shaft 16. The swash plate 20 is connected for operation to the lug plate 19 via a hinge mechanism 21 as will be described later.
  • the hinge mechanism 21 includes a pair of support arms 19A provided so as to protrude from the rear surface of the lug plate 19 toward the rear direction and a pair of guide pins 20A provided so as to protrude from the front surface of the swash plate 20 toward the front direction.
  • a pair of guide holes 19B are formed respectively at the distal portions of the support arms 19A, and a spherical portion 20B having a substantially spherical shape, which is formed at each distal portion of the guide pins 20A, is fitted into each of the guide holes 19B movably in a sliding manner.
  • the swash plate 20 is capable of connecting to the lug plate 19 for operation via the hinge mechanism 21, rotating integrally with the lug plate 19 and the drive shaft 16 by support of the drive shaft 16, and can be inclined with respect to a rotational central axis of the drive shaft 16 while sliding along the rotational central axis of the drive shaft 16.
  • the minimum inclination angle of the swash plate 20 is defined by a circular clip 22 fixed to the drive shaft 16 and a spring 23 disposed between the circular clip 22 and the swash plate 20. Note that the minimum inclination angle of the swash plate 20 indicates an inclination angle in the state where the angle made by the swash plate 20 and the rotational central axis of the drive shaft 16 is closest to 90°.
  • a plurality of cylinder bores 24 are formed in the cylinder block 11 in a penetrating manner along a direction of the rotational central axis of the drive shaft 16.
  • Single-head pistons 25 (compression member) are housed in the cylinder bores 24 for reciprocation. Front and rear openings of the cylinder bore 24 are closed by the piston 25 and the valve plate assembly 13, and a compression chamber, whose volume changes in accordance with the reciprocating motion of the piston 25, is defined in the cylinder bore 24.
  • Each piston 25 is firmly fixed to the outer periphery of the swash plate 20 via a pair of shoes 26. With this configuration, the rotational motion of the drive shaft 16 is converted into reciprocating motion or compression motion of each piston 25 via the lug plate 19, the swash plate 20, the shoes 26.
  • piston type compression mechanism is constituted of the drive shaft 16, the lug plate 19, the swash plate 20, the hinge mechanism 21, the pistons 25, and the shoes 26. Further, the lug plate 19, the swash plate 20, the hinge mechanism 21, and the shoes 26 constitute the conversion mechanism to convert the rotational motion of the drive shaft 16 into the compression motion of the pistons 25.
  • a suction chamber 27 and a discharge chamber 28 are defined and formed in the rear housing 14.
  • the front portions of the suction chamber 27 and the discharge chamber 28 are closed by the valve plate assembly 13.
  • Refrigerant gas (fluid) in the suction chamber 27 is introduced into the cylinder bore 24 (compression chamber) by the movement of each piston 25 from the rear portion to the front portion via a suction port 29 with opening a suction valve 30, which are formed in the valve plate assembly 13.
  • the low pressure refrigerant gas introduced into the cylinder bore 24 is compressed to a predetermined pressure by the movement of the piston 25 from the front portion to the rear portion, and is introduced into the discharge chamber 28 via a discharge port 31 with opening a discharge valve 32, which are formed in the valve plate assembly 13.
  • the suction chamber 27 and the discharge chamber 28 are connected by an external refrigerant circuit (not shown).
  • the refrigerant discharged from the discharge chamber 28 is introduced into the external refrigerant circuit.
  • the external refrigerant circuit performs heat exchange using the refrigerant.
  • the refrigerant discharged from the external refrigerant circuit is introduced into the suction chamber 27, introduced into the cylinder bore 24, and compressed again.
  • the housing is provided with a bleed passage 33 via which the crank chamber 15 communicates with the suction chamber 27. Additionally, the housing is provided with a supply passage 34 via which the discharge chamber 28 communicates with the crank chamber 15. A control valve 35 disposed on the supply passage 34 is capable of adjusting an opening degree of the supply passage 34.
  • crank chamber pressure Pc inner pressure of the crank chamber 15
  • the differential pressure between the crank chamber pressure Pc and the inner pressure of the compression chamber via the piston 25 is changed in accordance with variation of the crank pressure Pc, and the inclination angle of the swash plate 20 is varied.
  • stroke distance of the piston 25, that is, discharge capacity per one rotation of the drive shaft 16 is adjusted.
  • the state where the capacity of the compression chamber is the smallest is the state where the piston 25 is positioned at the top dead center
  • the state where the capacity of the compression chamber is the largest is the state where the piston 25 is positioned at the bottom dead center.
  • a portion where the piston 25 is positioned at the top dead center around the rotational central axis of the drive shaft 16 is referred to as a top dead center portion around the rotational central axis of the drive shaft 16
  • a portion where the piston 25 is positioned at the bottom dead center is referred to as a bottom dead center portion around the rotational central axis of the drive shaft 16.
  • the hinge mechanism 21 is provided at the top dead center portion around the rotational central axis of the drive shaft 16 (an upper portion of the drive shaft 16 in Fig. 1). Specifically, a pair of the support arms 19A and a pair of the pins 20A are provided at the top dead center portion around the rotational central axis of the drive shaft 16 with respect to the lug plate 19 and the swash plate 20, respectively.
  • a counter weight 19C for reducing the offset load of the lug plate 19 around the rotational central axis of the drive shaft 16, which is caused by the mass of a pair of the support arms 19A, is provided at the bottom dead center portion around the rotational central axis of the drive shaft 16.
  • a counter weight 20C for reducing the offset load of the swash plate 20 around the rotational central axis of the drive shaft 16, which is caused by the mass of a pair of the pins 20A is provided at the bottom dead center portion around the rotational central axis of the drive shaft 16.
  • the pulley 17 is fixed to the drive shaft 16 so as to integrally rotate with the drive shaft 16 in the state where the pulley is rotatably supported by a bearing 41 that is disposed on the outer circumferential surface of a support cylinder 40 provided on a front outer wall surface of the front housing 12.
  • the pulley 17 has the same rotational central axis as the drive shaft 16.
  • the pulley 17 includes a pulley body 42 made of resin.
  • the pulley body 42 is provided with a boss 43 attached to an outer ring of the bearing 41 and a cylindrical belt receiving portion 44 to which the belt 18 is hooked.
  • six recesses 45 (only one is shown in Fig. 1) as guide portions are formed in an area between the boss 43 and the belt receiving portion 44.
  • the recesses 45 are arranged at uniform intervals in a circumferential direction of the pulley 17. Further, three recesses 45 (a first recess 45A, a second recess 45B, a third recess 45C) among the six recesses 45 are arranged at the top dead center portion around the rotational central axis of the drive shaft 16, and the remaining three recesses 45 (a fourth recess 45D, a fifth recess 45E, a sixth recess 45F) are arranged at the bottom dead center portion around the rotational central axis of the drive shaft 16. As shown in Fig.
  • the first recess 45A, the second recess 45B and the third recess 45C are disposed in a clockwise direction from the left portion of the drawing in order, at the top dead center portion around the rotational central axis of the drive shaft 16.
  • the fourth recess 45D, the fifth recess 45E and the sixth recess 45F are disposed in the clockwise direction from the right portion of the drawing in order, at the bottom dead center portion around the rotational central axis of the drive shaft 16.
  • a guide surface 46 whose sectional shape on a plane orthogonal to a rotational central axis of the pulley 17 is in an arc-shape, is formed on each recess 45.
  • the guide surface 46 constitutes a part of an inner circumferential surface of a virtual cylinder with a radius r 1 whose center is an axis that is remote from the rotational central axis by a predetermined distance R 1 and is substantially parallel with the rotational central axis.
  • Rollers 47 (the diameter of the roller 47 is d 1 and the mass per one roller 47 is m 1 ) as mass bodies are housed by one in four of the six recesses 45.
  • the rollers 47 are housed in the three recesses 45 (the fourth recess 45D, the fifth recess 45E, the sixth recess 45F) at the bottom dead center portion around the rotational central axis of the drive shaft 16 and one recess 45 (the second recess 45B) at the top dead center portion around the rotational central axis of the drive shaft 16.
  • Each roller 47 is made of metal (iron in the present embodiment) of the same material (the same density), and formed in a cylindrical shape of the same shape and the same size, and thus setting the same mass.
  • Each roller 47 is housed in a state where it can roll in each recess 45 in the circumferential direction of the guide surface 46 along the guide surface 46.
  • Each roller 47 is prevented from falling outside each recess by a plate 48 fixed at the opening portion (front portion) of each recess 45 with screws, which is in a ring shape and made of resin.
  • each roller 47 When the vehicle engine E drives the compressor C, that is, during rotation of the drive shaft 16, centrifugal force works on each roller 47, and the roller is in the state where it contacts with the guide surface 46 (the state shown in Figs. 1, 2A and 2B). If torque fluctuation caused by torsional vibration (rotational vibration) of the drive shaft 16 occurs in this state, each roller 47 starts reciprocating motion in each recess 45 along the guide surface 46 (in the circumferential direction of the guide surface 46). Specifically, (center of gravity of) each roller 47 performs pendulum motion whose center is the central axis of the inner circumferential surface of the virtual cylinder, where the guide surface 46 constitutes a part thereof.
  • each roller 47 serves as a centrifugal pendulum when the vehicle engine E drives the compressor C.
  • arrangement position, a size and a mass of the rollers 47 in the pulley 17 are set in order to restrict the torque fluctuation (rotational vibration) by the pendulum motion of the rollers 47.
  • the rollers 47 serve to restrict the torque fluctuation (fluctuation width of the torque fluctuation) in frequency equal to the natural frequency of the rollers (centrifugal pendulum) 47. Therefore, the arrangement position, the size and the mass of the rollers 47 in the pulley 17 are set such that the natural frequency of the rollers 47 equals to the peak frequency of the torque fluctuation, so that the torque fluctuation at the peak is restricted and overall influence by the torque fluctuation is efficiently restricted.
  • the peak of the torque fluctuation indicates the peak of the fluctuation width in the torque fluctuation, that is, rotational order component.
  • R mentioned here is a distance between the rotational central axis of the pulley 17 (a rotational body provided with a mass body that performs pendulum motion) and the central axis of the pendulum motion of the roller 47 (mass body), and r is a distance between the central axis of the pendulum motion of the roller 47 and the center of gravity of the roller 47.
  • the central axis of the inner circumferential surface of the virtual cylinder where the guide surface 46 constitutes a part of the inner circumferential surface thereof, matches the central axis of the pendulum motion of the roller 47 (a fulcrum of the pendulum motion is on this central axis).
  • a distance R 1 between the rotational central axis of the pulley 17 and the central axis of the inner circumferential surface of the virtual cylinder corresponds to the distance R.
  • a distance between the central axis of the pendulum motion of the roller 47 and the center of gravity of the roller 47 is equal to a numerical value where a half of a diameter d 1 of the roller 47 is subtracted from the radius r 1 of inner circumferential surface of the virtual cylinder.
  • the difference ⁇ r 1 -(d 1 /2) ⁇ corresponds to the distance r.
  • sizes of R 1 , r 1 and d 1 are set to make the square root value of the ratio R 1 / ⁇ r 1 -(d 1 /2) ⁇ , which corresponds to the square root value of the ratio R/r, equal to the value of the n ⁇ N in order to restrict the peak in the torque fluctuation.
  • each piston 25 reciprocates in a stroke corresponding to the inclination angle of the swash plate 20, and suction, compression and discharge of refrigerant are sequentially repeated in each cylinder bore 24.
  • the torsional vibration generates the torque fluctuation.
  • the torque fluctuation is a cause to generate resonance in the compressor C itself and between external equipments (such as the vehicle engine E and an auxiliary machine) connected to the pulley 17 for operation via the belt 18 and the compressor C.
  • the rollers 47 provided for the pulley 17 begin pendulum motion.
  • the torque worked around the rotational central axis of the pulley 17 by the pendulum motion works to restrict the torque fluctuation.
  • the offset load of the pulley 17 based on the fact that the rollers 47 are arranged at the bottom dead center portion around the rotational central axis of the drive shaft 16 more than the top dead center portion works to cancel the offset load of the conversion mechanism, which is caused by the fact that the hinge mechanism 21 is provided at the top dead center portion around the rotational central axis of the drive shaft 16.
  • Embodiments are not limited to the above-described ones, but may be in the following modes, for example.
  • the rotational order component corresponding to the rollers at the bottom dead center portion may be set at the lower order than the rotational order component corresponding to the rollers at the top dead center portion.
  • the mass per unit of the rollers at the bottom dead center portion may be set to be smaller than the mass per unit of the rollers at the top dead center portion.
  • the number of the rollers at the bottom dead center portion may be set to be smaller than the number of the rollers at the top dead center portion.
  • a length in a direction of the rotational central axis for a part of a plurality of the rollers (47, 50) may be different from the other rollers. Accordingly, the mass per unit for a part of a plurality of the rollers (47, 50) can be made different from the other rollers by the difference in lengths. Therefore, the mass difference can cancel the offset load of the conversion mechanism around the rotational central axis of the drive shaft 16. According to the present structure, the mass per unit can be made different from each other even if the diameters of the rollers (47, 50) are set in a uniform size, for example. In this case, a structure is made as shown in Fig. 7. The structure of Fig.
  • the rollers 47 are housed in all the recesses 45. Further, the length (L 2 ) in the direction of the rotational central axis of the recesses (the fourth recess 45D, the fifth recess 45E, the sixth recess 45F) is set to be longer than the length (L 1 ) in the direction of the rotational central axis of the recesses (the first recess 45A, the second recess 45B, the third recess 45C). Note that the diameters of all the rollers 47 are set equally (d 1 ). Thus, the mass distribution of the rollers 47 in the pulley 17 is set to be larger at the bottom dead center portion around the rotational central axis of the drive shaft 16 than the top dead center portion.
  • material for a part of a plurality of the rollers (47, 50) may be material having different density from the other rollers. This can make the mass per unit for a part of a plurality of the rollers (47, 50) different from the other rollers. Therefore, the mass difference can cancel the offset load of the conversion mechanism around the rotational central axis of the drive shaft 16. According to the present structure, the mass per unit can be made different from each other even if the shape and the size of the rollers (47, 50) are the same, for example.
  • rollers (47, 50) may be formed using copper, tungsten.
  • the pulley body 42 may be formed using metal.
  • the mass distribution of the pulley body 42 around the rotational central axis of the drive shaft 16 may be adjusted by varying the shape of the lightened metal.
  • the mass body may be formed in a spherical shape.
  • the rollers (47, 50) that roll along the guide surface 46 of the recesses 45 formed in the pulley 17 are made to perform pendulum motion.
  • the pulley may be provided with mass bodies that perform pendulum motion using a support shaft fixed to the pulley as a fulcrum.
  • the mass body itself is provided with the support shaft, and the support shaft may be inserted into a hole formed on the pulley to support the mass body on the pulley in such a manner that pendulum motion can be performed.
  • a plurality of mass bodies is provided for the rotor.
  • a structure where only one mass body is provided may be used.
  • the one mass body is provided so as to cancel the offset load of the conversion mechanism around the rotational central axis of the drive shaft 16.
  • the mass bodies are provided to cope with one or two rotational order component.
  • the mass bodies may be structured to cope with three or more rotational order component.
  • the ratio R/r is set to cope with the rotational order component in the rotational vibration that the compressor C generates.
  • the ratio R/r may be set in order to cope with the rotational order component in the rotational vibration that the vehicle engine E or the auxiliary machine (a rotary machine such as an oil pump for power steering), which are connected to the compressor C for operation via power transmission member such as the belt 18, generates.
  • means for assembly and positioning in the circumferential direction of the drive shaft 16 between the pulley 17 and the drive shaft 16 may be provided. With this means, working efficiency is improved when the pulley 17 is assembled on the drive shaft 16.
  • the cylinder bores 24 in the compressor C may be set in any number.
  • the number of the cylinder bores 24 is set to any of 3 to 7 for the compressor used in a vehicle air conditioner in many cases.
  • the torque fluctuation quantity of rotational vibration in the drive shaft 16 tends to increase comparing to the case where the number is set to 4 or more.
  • rotational vibration restricting effect by the mass bodies works particularly efficiently in the compressor where the number of the cylinder bores 24 is set to 3.
  • the pulley 17 may be provided for a double-head piston type compressor where double-head pistons perform compression operation in the cylinder bores provided on both front and rear sides sandwiching the crank chamber, not for a single-head piston type compressor where single-head piston performs compression operation.
  • the compressor C may be a type in which a cam plate is supported by the drive shaft so as to rotate and wobble with respect to the drive shaft, which is a wobble type compressor, for example, instead of the structure in which the cam plate (swash plate 20) integrally rotates with the drive shaft 16.
  • a sprocket and a gear may be applied as the rotation body other than the pulley.
  • the rotation body may be applied for a rotational member housed in the housing of the compressor C.
  • the mass body may be provided for the lug plate 19 connected for operation to the drive shaft 16 in the housing or for another member particularly provided, and thus the rotational vibration on the drive shaft 16 may be restricted.
  • the central axis of the pendulum motion of the mass body may not necessarily be parallel with the rotational central axis of the rotation body provided with the mass body.
  • the central axis of the pendulum motion may be inclined with respect to the rotational central axis of the rotation body within a scope where a desired effect can be obtained in restriction of the transferred torque fluctuation.
  • a distance R s (described below) is set as a distance between the center of the pendulum motion and the rotational central axis of the rotation body, for example, in the state where the central axis of the pendulum motion is inclined with respect to the rotational central axis of the rotation body.
  • a distance between an intersectional point made by a plane, which is perpendicular to the central axis of the pendulum motion and passes the center of gravity of the mass body, and the central axis of the pendulum motion, and the rotational central axis of the rotation body is set as the distance R s .
  • a compressor includes a drive shaft, a conversion mechanism, a rotation body and a mass body.
  • the conversion mechanism converts rotational motion of the drive shaft into compression motion of a compression member in a compression mechanism.
  • the rotation body is provided with the drive shaft so as to integrally rotate with the drive shaft.
  • the drive shaft and the rotation body have a rotational central axis.
  • the mass body is provided with the rotation body.
  • the mass body performs pendulum motion whose center is an axis that is remote from the rotational central axis by a predetermined distance and that is substantially parallel with the rotational central axis.
  • the compressor is characterized in that the mass body is provided to cancel offset load of the conversion mechanism around the rotational central axis of the drive shaft.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP03005001A 2002-03-06 2003-03-05 Ausgleichsystem für verdichter Withdrawn EP1342920A3 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2002060501 2002-03-06
JP2002060501A JP2003254233A (ja) 2002-03-06 2002-03-06 圧縮機

Publications (2)

Publication Number Publication Date
EP1342920A2 true EP1342920A2 (de) 2003-09-10
EP1342920A3 EP1342920A3 (de) 2003-12-10

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EP03005001A Withdrawn EP1342920A3 (de) 2002-03-06 2003-03-05 Ausgleichsystem für verdichter

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JP (1) JP2003254233A (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008009446A1 (de) * 2006-07-19 2008-01-24 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH System mit einem verdichter und einem verbraucher in einem kraftfahrzeug
CN109209817A (zh) * 2018-11-20 2019-01-15 泉州苗亿自动化机械有限公司 一种静音无油空压机

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2017133549A (ja) * 2016-01-26 2017-08-03 トヨタ自動車株式会社 捩り振動低減装置

Citations (7)

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Publication number Priority date Publication date Assignee Title
US6076449A (en) * 1997-03-31 2000-06-20 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable displacement compressor
US6247902B1 (en) * 1997-11-28 2001-06-19 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Torsional vibration attenuating structure in compressor
DE10013652A1 (de) * 2000-03-18 2001-09-20 Mannesmann Sachs Ag Schwingungsdämpfungseinrichtung
US20010025762A1 (en) * 2000-01-31 2001-10-04 Mannesmann Sachs Ag Torsional vibration damper
WO2002012751A2 (de) * 2000-08-09 2002-02-14 Hasse & Wrede Gmbh Drehschwingungsdämpfer
EP1270941A2 (de) * 2001-06-28 2003-01-02 Kabushiki Kaisha Toyota Jidoshokki Kraftübertragungsmechanismus für Verdichter
EP1286050A2 (de) * 2001-08-23 2003-02-26 Kabushiki Kaisha Toyota Jidoshokki Rotationsdämpfer

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6076449A (en) * 1997-03-31 2000-06-20 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable displacement compressor
US6247902B1 (en) * 1997-11-28 2001-06-19 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Torsional vibration attenuating structure in compressor
US20010025762A1 (en) * 2000-01-31 2001-10-04 Mannesmann Sachs Ag Torsional vibration damper
DE10013652A1 (de) * 2000-03-18 2001-09-20 Mannesmann Sachs Ag Schwingungsdämpfungseinrichtung
WO2002012751A2 (de) * 2000-08-09 2002-02-14 Hasse & Wrede Gmbh Drehschwingungsdämpfer
EP1270941A2 (de) * 2001-06-28 2003-01-02 Kabushiki Kaisha Toyota Jidoshokki Kraftübertragungsmechanismus für Verdichter
EP1286050A2 (de) * 2001-08-23 2003-02-26 Kabushiki Kaisha Toyota Jidoshokki Rotationsdämpfer

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008009446A1 (de) * 2006-07-19 2008-01-24 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH System mit einem verdichter und einem verbraucher in einem kraftfahrzeug
US8337169B2 (en) 2006-07-19 2012-12-25 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh System with a compressor and with a consumer in a motor vehicle
CN109209817A (zh) * 2018-11-20 2019-01-15 泉州苗亿自动化机械有限公司 一种静音无油空压机
CN109209817B (zh) * 2018-11-20 2023-09-29 泉州苗亿自动化机械有限公司 一种静音无油空压机

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EP1342920A3 (de) 2003-12-10

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