US20030002991A1 - Compressor - Google Patents
Compressor Download PDFInfo
- Publication number
- US20030002991A1 US20030002991A1 US10/183,719 US18371902A US2003002991A1 US 20030002991 A1 US20030002991 A1 US 20030002991A1 US 18371902 A US18371902 A US 18371902A US 2003002991 A1 US2003002991 A1 US 2003002991A1
- Authority
- US
- United States
- Prior art keywords
- drive shaft
- rotary drive
- compressor
- rotating body
- compressor according
- 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
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
- F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
- F16F15/145—Masses mounted with play with respect to driving means thus enabling free movement over a limited range
-
- 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
-
- 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
- F04B39/0088—Pulsation and noise damping means using mechanical tuned resonators
Definitions
- the present invention relates to a compressor, and more particularly, to a compressor that reduces resonance.
- a conventional compressor has a damper mechanism.
- the damper mechanism reduces torque fluctuations of a rotary drive shaft, which drives the compressor, and reduces vibrations of the compressor.
- Japanese Laid-Open Patent Publication Nos. 2000-213600 and 2000-274489 describe conventional damper mechanisms.
- One example of the convention damper mechanism is a dynamic damper, which includes a mass body that reciprocates along an arcuate path. Further, the conventional damper mechanism is arranged on a pulley that transmits external drive force to the rotary drive shaft of the compressor.
- the conventional damper mechanism which is arranged on the pulley, makes it difficult to reduce the size of the pulley. Since the pulley is located at the outer side of a compressor housing, the pulley and the mass body produce a hitting noise. Thus, the noise level of the compressor is relatively high. Further, the damper mechanism, which is located outside the housing, may rust or collect dust. This may cause the compressor to function abnormally or may lower the durability of the compressor.
- the present invention provides a compressor including a housing, a rotary drive shaft rotatably supported by the housing, and a compression mechanism accommodated in the housing.
- the compressor includes a rotating body connected to the rotary drive shaft and arranged in the housing.
- a mass body is supported by the rotating body at a position radially separated from an axis of the rotating body by a predetermined distance.
- the mass body is supported in a manner permitting pendulum movement.
- FIG. 1 is a cross-sectional view of a compressor according to a first embodiment of the present invention
- FIG. 2 is a front view of a lug plate of the compressor of FIG. 1;
- FIG. 3 is a cross-sectional view showing a modification of a swash plate
- FIG. 4 is a cross-sectional view of a compressor according to a second embodiment of the present invention.
- FIG. 5 is a partial cross-sectional view of a modification of a lug plate.
- FIG. 6 is front view of the lug plate of FIG. 5.
- variable displacement compressor 100 which is used in a vehicle air-conditioner, according to a first embodiment of the present invention will now be discussed with reference to FIGS. 1 and 2.
- the left side is defined as the front side
- the right side is defined as the rear side.
- the compressor 100 includes a cylinder block 11 , a front housing 12 , which is coupled to the front end of the cylinder block, and a rear housing 14 , which is coupled to the rear end of the cylinder block 11 with a valve plate 13 arranged in between.
- the cylinder block 11 , the front housing 12 , the valve plate 13 , and the rear housing 14 define a housing of the compressor 100 .
- a crank chamber 15 is defined in the cylinder block 11 and the front housing 12 . Further, the cylinder block 11 and the front housing 12 rotatably support a rotary drive shaft 16 , which extends through the crank chamber 15 .
- a pulley 17 is connected to the front end of the rotary drive shaft 16 , which projects out of the front housing 12 .
- a vehicle engine E drives the rotary drive shaft 16 by means of a belt 18 , which is connected to the pulley 17 .
- a disk-like lug plate 19 is connected to the rotary drive shaft 16 by means of a friction damper, or cylindrical rubber damper 19 A, in the crank chamber 15 .
- a swash plate 20 is accommodated in the crank chamber 15 .
- the swash plate 20 is connected to the lug plate 19 , or rotating body, by means of a hinge mechanism 21 .
- the swash plate 20 rotates integrally with the rotary drive shaft 16 .
- the swash plate 20 is supported so that it slides along the rotary drive shaft 16 and inclines relative to the rotary drive shaft 16 .
- a ring 22 which is fixed to the rotary drive shaft 16
- a spring 23 which is arranged between the ring 22 and the swash plate 20 , determines the minimum inclination of the swash plate 20 .
- the inclination of the swash plate 20 refers to the angle of the swash plate 20 relative to a hypothetical plane that is perpendicular to the axis of the rotary drive shaft 16 .
- the minimum inclination is the angle of the swash plate 20 when it is closest to the hypothetical plane.
- a plurality of cylinder bores 24 extend parallel to the axis of the rotary drive shaft 16 in the cylinder block 11 .
- a single-headed piston 25 reciprocates in each cylinder bore 24 .
- the piston 25 , the cylinder bore 24 , and the valve plate 13 define a compression chamber.
- the volume of the compression chamber varies in accordance with the position of the piston 25 .
- Each piston 25 is connected to the peripheral portion of the swash plate 20 by means of shoes 26 . Accordingly, the rotation of the rotary drive shaft 16 , or the rotation of the inclined swash plate 20 , is converted to the linear reciprocation of the pistons 25 .
- the cylinder block 11 (cylinder bores 24 ), the rotary drive shaft 16 , the lug plate 19 , the swash plate 20 , the hinge mechanism 21 , the piston 25 , and the shoes 26 form a variable displacement piston compression mechanism.
- a suction chamber 27 and a discharge chamber 28 are defined in the rear housing 14 .
- the valve plate 13 closes the front sides of the suction chamber 27 and the discharge chamber 28 .
- refrigerant gas is drawn into the associated cylinder bore 24 (compression chambers) from the suction chamber 27 through a suction port 29 and a suction valve 30 , which are formed in the valve plate 13 .
- the low-pressure refrigerant gas in the cylinder bore 24 is compressed to a predetermined pressure and released into the discharge chamber 28 through a discharge port 31 and a discharge valve 32 , which are formed in the valve plate 13 .
- the discharge chamber 28 is connected to the suction chamber 27 through an external refrigerant circuit (not shown).
- the refrigerant is discharged from the discharge chamber 28 and sent into the external refrigerant circuit. After exchanging heat in the external refrigerant circuit, the refrigerant is returned to the suction chamber 27 from the external refrigerant circuit.
- a bleeding passage 33 which connects the crank chamber 15 and the suction chamber 27
- a gas supply passage 34 which connects the discharge chamber 28 and the crank chamber 15
- a control valve 35 which adjusts the opening degree of the gas supply passage 34 , is arranged in the gas supply passage 34 .
- the control valve 35 changes the balance between the amount of refrigerant gas drawn into the crank chamber 15 and the amount of refrigerant gas discharged from the crank chamber 15 .
- the control valve 35 determines the pressure of the crank chamber 15 (crank pressure Pc) by adjusting the balance between the amount of high-pressure refrigerant gas sent into the crank chamber 15 from the discharge chamber 28 and the amount of refrigerant gas sent out of the crank chamber 15 to the suction chamber 27 through the bleeding passage 33 .
- crank pressure Pc crank pressure of the compression chambers, which are the pressures acting on the ends of the pistons 25 , alters the inclination of the swash plate 20 . This changes the stroke of the pistons 25 and varies the displacement of the compressor.
- a lubricant oil mist which is suspended in the refrigerant gas, lubricates moving parts in the crank chamber 15 .
- FIG. 2 is a front view of the lug plate 19 .
- a cover 44 is removed from the lug plate 19 in the state of FIG. 2.
- the lug plate 19 has an axis 19 ⁇ , which coincides with the axis of the rotary drive shaft 16 .
- each receptacle 41 has a circumferential surface (guide surface) 42 , which guides the rolling of the associated roller 43 . More specifically, each receptacle 41 is a cylindrical bore having an axis 41 ⁇ , which is separated from the axis 19 ⁇ of the lug plate 19 by a predetermined distance R 1 . The radius of the cylindrical bore is r 1 . Thus, the radius of curvature of each guide surface 42 is equal to radius R 1 .
- each roller 43 is movable along the guide surface 42 of the associated receptacle 41 . More specifically, the diameter d 1 of each roller 43 is smaller than the diameter 2r 1 of each receptacle 41 , and the length of each roller 43 in the axial direction is slightly less than the depth of each receptacle 41 (the depth in the axial direction of the lug plate 19 ).
- the annular cover 44 is attached to the front end of the lug plate 19 . The cover 44 prevents the rollers 43 from falling out of the guide receptacles 41 .
- the cover 44 also functions as a race of a thrust bearing 45 and restricts forward axial movement of the lug plate 19 .
- each roller 43 i.e., the center of gravity of each roller 43 ) starts a pendulum movement about the axis 41 ⁇ of the receptacle 41 . Accordingly, each roller 43 functions as a centrifugal pendulum when the compressor 100 is driven.
- each roller 43 and the position where each roller 43 is arranged on the lug plate 19 i.e., the position and dimension of each receptacle 41 ) is set so that the pendulum movement of each roller 43 suppresses torque fluctuation.
- each roller 43 suppresses torque fluctuations having a frequency that is equal to the inherent frequency of the roller 43 . It is thus preferred that the dimension, mass, and position of the roller 43 be set so that the inherent frequency of the roller 43 be equal to the frequency of the torque fluctuation peak. In this case, vibrations at the torque fluctuation peak are reduced. This effectively reduces the influence of torque fluctuations.
- the torque fluctuation peak refers to the peak of the fluctuating amount of torque, that is, the rotation order component.
- the vibrations of the torque fluctuation and the inherent vibrations of the rollers 43 are proportional to the angular velocity ⁇ 1 of the rotary drive shaft 16 , which is related with the rotating speed of the rotary drive shaft 16 .
- the torque fluctuation is formed from various types of peaks that appear periodically.
- the frequency of the first peak is represented by ( ⁇ 1 /2 ⁇ n) ⁇ N.
- ( ⁇ 1 /2 ⁇ ) represents the rotation of the rotary drive shaft 16 per unit time
- N represents the number of cylinder bores 24 .
- the nth peak of the nth largest torque fluctuation appears at a cycle that differs from the predetermined first cycle.
- the frequency of such cycle is represented by n ⁇ ( ⁇ 1 /2 ⁇ ) ⁇ N. It has been confirmed through experiments that among the torque fluctuation peaks, the frequency of the nth (n being a natural number) peak has a tendency to have the same value as product n ⁇ ( ⁇ 1 /2 ⁇ ) ⁇ N.
- the inherent vibration of the roller 43 is calculated from the product of the rotation of the rotary drive shaft 16 per unit time ( ⁇ 1 /2 ⁇ ) and the square root of ratio R/r.
- R represents the distance between the axis of the lug plate 19 and the center axis 41 ⁇ of the pendulum movement of the roller 43
- r represents the distance between the center axis 41 ⁇ of the pendulum movement of the roller 43 and the center of gravity g 1 of the roller 43 .
- the mass m of the roller is maximized to decrease the values of R, r, and ⁇ . This enables the torque T to be increased, while preventing the lug plate 19 from being enlarged.
- the axis 41 ⁇ of each receptacle 41 coincides with the center of the pendulum movement of the associated roller 43 .
- the center of the pendulum movement of each roller 43 is located along the associated axis 41 ⁇ . Accordingly, the distance R 1 between the axis 41 ⁇ and the axis 19 ⁇ of the lug plate 19 corresponds to R in equation 1.
- the distance between the center of pendulum movement of the roller 43 , or the axis 41 ⁇ of the receptacle 41 , and the center of gravity g 1 of the roller 43 is equal to a value obtained by subtracting half the diameter d 1 of the roller 43 from the radius r 1 of the receptacle 41 . Accordingly, the difference ⁇ r 1 ⁇ (d 1 /2) ⁇ corresponds to r in equation 1.
- the roller 43 is considered to be a particle in which the mass of the roller 43 concentrates at the center of gravity g 1 .
- the opening degree of the control valve 35 decreases, the amount of high pressure refrigerant gas supplied to the crank chamber 15 via the gas supply passage 34 from the discharge chamber 28 decreases. This decreases the crank chamber pressure Pc, increases the inclination of the swash plate 20 , and increases the displacement of the compressor 100 .
- the opening degree of the control valve 35 increases, the amount of high pressure refrigerant gas supplied to the crank chamber 15 via the gas supply passage 34 from the discharge chamber 28 increases. This increases the crank chamber pressure Pc, decreases the inclination of the swash plate 20 , and decreases the displacement of the compressor 100 .
- each roller 43 starts the pendulum movement. Due to the pendulum movement, the torque acting about the axis 19 ⁇ of the lug plate 19 functions to suppress the torque fluctuation.
- the inherent vibrations of the roller 43 are set to be equal to the vibrations at the highest peak of the torque fluctuation. This suppresses the vibrations at the highest peak of the torque fluctuation and, as a whole, effectively reduces torque fluctuations of the lug plate 19 .
- the lug plate 19 is connected to the rotary drive shaft 16 by a rubber damper 19 A.
- the torque fluctuation transmitted from the lug plate 19 to the rotary drive shaft 16 is further reduced by the rubber damper 19 A.
- resonance caused by torque fluctuations is effectively suppressed.
- the rubber damper 19 A effectively reduces relatively high frequency torque fluctuations.
- the pendulum movement of the rollers 43 effectively reduces relatively low frequency torque fluctuations.
- the first embodiment has the advantages described below.
- the rollers 43 are attached to the lug plate 19 .
- Each roller 43 performs a pendulum movement about a point ( 41 ⁇ ), which is separated from the axis 19 ⁇ of the lug plate 19 by the predetermined distance R 1 .
- the pendulum movement of each roller 43 suppresses resonance produced in the compressor 100 and resonance produced between the compressor 100 and a rotary mechanism, which is connected to the compressor 100 by the belt 18 .
- the rollers 43 are accommodated in the housing.
- rotating members located on the outer side of the housing such as the pulley 17 , may easily be reduced in size.
- the noise produced when contact occurs between the receptacles 41 , the cover 44 , and the rollers 43 is absorbed in the housing.
- the noise level of the compressor 100 is relatively low.
- the rollers 43 are not exposed to the environment outside the housing.
- abnormalities resulting from rusting of the rollers 43 or dust collecting on the rollers 43 do not occur. Accordingly, resonance is reduced and the compressor 100 has improved durability and weather resistance.
- rollers 43 are arranged in the crank chamber 15 .
- the rollers 43 are lubricated by the oil mist, which lubricates the compression mechanism.
- the rollers 43 have a round cross-section and roll along the associated curved guide surfaces 42 , which are formed in the lug plate 19 . Since the rollers 43 easily perform the pendulum movement along the associated guide surfaces 42 , vibrations of the compressor 100 and resonance produced between the rotating mechanism and the compressor is suppressed.
- the rubber damper 19 A is arranged between the lug plate 19 and the rotary drive shaft 16 .
- the damper effect of the rubber dampers 19 A is also obtained. This effectively suppresses resonance.
- rollers 43 are arranged in the lug plate 19 , which inclinably supports the swash plate 20 .
- an additional rotating body does not have to be provided for the rollers 43 . Accordingly, resonance is suppressed without enlarging the compressor 100 .
- a fixed displacement compressor 200 according to a second embodiment of the present invention will now be discussed.
- the compressor 200 has two cylinder blocks 51 , which are connected to each other.
- the front housing 52 is connected to the front end of the front cylinder block 51 with a valve plate 54 arranged in between.
- a rear housing 53 is connected to the rear end of the rear cylinder block 51 with a valve plate 54 arranged in between.
- Bolt holes 55 extend through the front housing 52 and the two cylinder blocks 51 .
- a bolt 56 which has a threaded portion 56 A on its distal end, is inserted through each bolt hole 55 to screw the threaded portion 56 A into a threaded hole 55 A.
- the bolt 56 fastens the front housing 52 and the rear housing 53 to the cylinder blocks 51 .
- the cylinder block 51 , the front housing 52 , and the rear housing 53 form a housing of the compressor 200 .
- a rotary drive shaft 57 is rotatably supported in the cylinder blocks 51 and the front housing 52 by a pair of radial bearings 51 A.
- the front end of the rotary drive shaft 57 projects outward from the front housing 52 through a center hole 52 A, which is formed in the front housing 52 .
- the front end of the rotary drive shaft 57 is connected to a power transmission mechanism (not shown).
- the rotary drive shaft 57 is driven by an external drive source, such as a vehicle engine, by means of the power transmission mechanism.
- a lip seal assembly 52 B which prevents the leakage of refrigerant gas, is attached to the front housing 52 to seal the space between the rotary drive shaft 57 and the wall of the center hole 52 A.
- a plurality of (an N number of) equally spaced cylinder bores 51 B extend parallel to the rotary drive shaft 57 through the two cylinder blocks 51 .
- a double-headed piston 59 reciprocates in each cylinder bore 51 B.
- Compression chambers 51 C are defined between the end surfaces of the pistons 59 , the valve plates 54 , and the cylinder bores 51 B.
- a crank chamber 58 is connected to an external refrigerant circuit (not shown).
- the crank chamber 58 is supplied with relatively low refrigerant gas from the external refrigerant circuit.
- the crank chamber 58 serves as part of a refrigerant passage in the housing.
- a swash plate 60 which has a sleeve 60 A and a disk 60 B, are accommodated in the crank chamber 58 .
- the sleeve 60 A is fitted on the rotary drive shaft 57 .
- the disk 60 B extends radially from the sleeve 60 A.
- the peripheral portion of the disk 60 B is connected to the middle portion of each piston 59 by shoes 61 .
- Two thrust bearings 62 are arranged between the cylinder blocks 51 and the front and rear sides of the sleeve 60 A.
- the two thrust bearings 62 rotatably hold the swash plate 60 in the two cylinder blocks 51 .
- the swash plate 60 converts the rotation of the rotary drive shaft 57 to the reciprocation of the pistons 59 .
- the angle between the swash plate 60 and the rotary drive shaft 57 is fixed.
- the stroke of the pistons 59 is fixed.
- the shoes 61 and the swash plate 60 form a crank mechanism.
- the crank mechanism, the cylinder blocks 51 (cylinder bores 51 B), the pistons 59 , and the rotary drive shaft 57 form a piston compression mechanism.
- Suction chambers 63 are defined in the front and rear housings 52 , 53 .
- the suction chamber 63 is connected to the bolt holes 55 through a communication hole (not shown). Accordingly, the suction chambers 63 are connected to the crank chamber 58 through the bolt holes 55 .
- Discharge chambers 64 are defined at the inner sides of the suction chambers 63 in the front and rear housings 52 , 53 .
- the discharge chamber 64 is connected to an external refrigerant circuit.
- Each valve plate 54 includes a plurality of suction ports 65 , which are formed in correspondence with the associated suction chambers 63 , and a plurality of suction valves 66 , which open and close the associated suction ports 65 .
- the corresponding suction valve 66 opens to draw refrigerant gas into the compression chamber 51 C from the corresponding suction chamber 63 .
- each valve plate 54 includes a plurality of discharge ports 67 , which are formed in correspondence with the associated discharge chambers 64 , and a plurality of discharge valves 68 , which open and close the associated discharge ports 67 .
- the corresponding discharge valve 68 opens to discharge refrigerant into the corresponding discharge chamber 64 .
- the crank chamber 58 , the bolt holes 55 , the suction chambers 63 , the suction ports 65 , the compression chambers 51 C, the discharge ports 67 , and the discharge chambers 64 form the refrigerant passage in the housing.
- Components in the refrigerant circuit in the housing are lubricated by oil mist, which circulates with refrigerant gas in the passage.
- the disk 60 B of the swash plate 60 has a plurality of guides, or receptacles 60 C (only two shown in FIG. 4).
- a cylindrical mass body, or roller 69 is accommodated in each receptacle 60 C.
- a cover 60 D is attached to the swash plate 60 to close the opening of the receptacles 60 C.
- Each roller 69 rolls along a guide surface 60 E of the receptacles 60 C.
- the guide surface 60 E is arcuate.
- R represent the distance between the axis of the swash plate 60 and the center point of the pendulum movement of each roller 69
- r represents the distance between the center point of the pendulum movement of each roller 69 and the center of gravity of the roller 69 .
- the second embodiment has the advantages described below.
- first and second embodiments may be modified as described below.
- the lug plate 19 of the first embodiment may be directly connected to the rotary drive shaft 16 without the rubber damper 19 A.
- a spring such as a metal plate spring, may be used in lieu of the rubber damper 19 A in the first embodiment.
- the lug plate 19 has a recess formed in a surface corresponding to the cylindrical surface of the rotary drive shaft 16
- the rotary drive shaft 16 has a recess formed in a surface corresponding to the lug plate 19 .
- One end of a square plate spring is received in the recess of the lug plate 19 .
- the other end of the plate spring is received in the recess of the rotary drive shaft 16 . This connects the lug plate 19 and the rotary drive shaft 16 .
- the cover 44 is also used as the race of the thrust bearing 45 .
- the cover 44 does not have to be used as a race.
- a member that differs from the race of the thrust bearing 45 prevents rollers 43 from falling out of the receptacles 41 .
- the swash plate 20 rotates integrally with the rotary drive shaft 16 .
- the present invention may also be applied to a wobble plate compressor in which a cam plate, or a wobble plate, rotates relative to a rotary drive shaft.
- the present invention may be applied to a fixed displacement compressor having pistons with a fixed stroke in lieu of the compressor 100 of the first embodiment.
- the swash plate 60 of the second embodiment may be modified as shown in FIG. 3. More specifically, the swash plate 60 of FIG. 3 has cylindrical bores, the axes of which are parallel to the axis of the swash plate 60 . In this case, a roller 69 rolls along a guide surface 60 E of each cylinder bore to perform a pendulum movement. When the swash plate 60 is rotating, the movement of the roller 69 toward the rotary drive shaft 57 is restricted. This effectively suppresses resonance.
- FIG. 3 shows the swash plate 60 in a state before it is attached to the rotary drive shaft 57 .
- the swash plate 60 of the second embodiment may be connected to the rotary drive shaft 57 by means of a friction damper.
- a friction damper In such a case, the damper effect obtained by the cooperation between the rollers 69 and the friction damper effectively suppresses resonance.
- the lug plate 19 has receptacles 82 , each of which accommodates a mass body, or a pendulum 81 .
- Each receptacle 82 has a inner surface 82 A to which a pivot pin 83 is fixed parallel to the axis of the lug plate 19 .
- the pivot pin 83 pivotally supports one of the pendulums 81 .
- the pendulum 81 performs the pendulum movement about the pivot pin 83 in accordance with the rotational vibrations produced when the rotary drive shaft 16 rotates.
- R represents the distance between the axis of the lug plate 19 and each pivot pin 83
- r represents the distance between the pivot pin 83 and the center of gravity of each pendulum 81 .
- each pendulum 81 is supported by the associated pivot pin 83 , which is fixed to the lug plate 19 .
- the pivot pin 83 may be fixed to the pendulum 81 , and the pivot pin 83 may be inserted in a hole formed in the lug plate 19 .
- the pendulums 81 are arranged on the lug plate 19 .
- the pendulums 81 may be arranged on the swash plate 60 of the second embodiment.
- the present invention may be applied to a member other than the lug plate 19 or the swash plate 60 as long as the member is a rotating body connected to a rotary drive shaft that is arranged in a housing of a compressor.
- the mass bodies 43 , 69 , 81 may be changed to spherical bodies.
- the square root of the ratio R/r may be set so that it is equalized with the value of product n ⁇ N when n is a natural number of two or greater (e.g., 2 or 3).
- the number of mass bodies does not have to be the same as the number of cylinder bores of the compressor as long as there is at least one mass body.
- the value corresponding to the square root of the ratio R/r may differ between each mass body (rollers 43 , 69 , pendulum 81 ) In such a case, since multiple values, which correspond to the ratio R/r, are set, the fluctuating range of the peaks (rotation order) of the torque fluctuation is suppressed.
- a plurality of products n ⁇ N may correspond to a plurality of the square roots of R/r, respectively.
- more than two peaks of the torque fluctuation starting from the largest one (in this case, three) are suppressed. This further improves the resonance suppressing effect.
- the above calculations be performed by considering the mass body as an object having a volume and not as a particle.
- the ratio R/r may be replaced by ratio 2R/3r. This would include the inertial weight of the mass body.
- torque T is obtained from the next equation. In the equation, the vibrations at the peak of the torque fluctuation coincide with the inherent vibrations of the rollers 43 .
- ratio R/r is replaced by ratio 5R/7r to take the inertial weight into consideration.
- the level of the torque T when the vibrations at the peak of the torque fluctuation in this case matches the inherent vibrations of the spherical mass body is obtained from the next equation.
- the present invention may be applied to a rotary compressor, such as a scroll compressor.
- the mass body is arranged on a rotating body accommodated in the housing of the compressor.
- the present invention may be applied to a compressor having an electric rotating device, such as a motor, arranged in the housing to drive the rotary drive shaft.
- the mass body may be arranged in a rotor of the electric rotating device.
- the axis of the pendulum movement of the mass body does not have to be parallel to the axis of the rotating body.
- the axis of the pendulum movement may be inclined relative to the axis of the rotating body.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Compressor (AREA)
Abstract
A compressor that employs rollers to suppress resonance. The compressor includes a lug plate, which is connected to a rotary drive shaft by means of a rubber damper. The lug plate is arranged in a crank chamber. The lug plate has receptacles, which guide the pendulum movement of the rollers. When the rotary drive shaft rotates, the pendulum movement of each roller suppresses the resonance of the compressor.
Description
- The present invention relates to a compressor, and more particularly, to a compressor that reduces resonance.
- A conventional compressor has a damper mechanism. The damper mechanism reduces torque fluctuations of a rotary drive shaft, which drives the compressor, and reduces vibrations of the compressor. Japanese Laid-Open Patent Publication Nos. 2000-213600 and 2000-274489 describe conventional damper mechanisms. One example of the convention damper mechanism is a dynamic damper, which includes a mass body that reciprocates along an arcuate path. Further, the conventional damper mechanism is arranged on a pulley that transmits external drive force to the rotary drive shaft of the compressor.
- However, the conventional damper mechanism, which is arranged on the pulley, makes it difficult to reduce the size of the pulley. Since the pulley is located at the outer side of a compressor housing, the pulley and the mass body produce a hitting noise. Thus, the noise level of the compressor is relatively high. Further, the damper mechanism, which is located outside the housing, may rust or collect dust. This may cause the compressor to function abnormally or may lower the durability of the compressor.
- It is an object of the present invention to provide a compressor that easily reduces the size of a pulley, reduces noise and resonance, and improves durability.
- To achieve the above object, the present invention provides a compressor including a housing, a rotary drive shaft rotatably supported by the housing, and a compression mechanism accommodated in the housing. The compressor includes a rotating body connected to the rotary drive shaft and arranged in the housing. A mass body is supported by the rotating body at a position radially separated from an axis of the rotating body by a predetermined distance. The mass body is supported in a manner permitting pendulum movement.
- Other aspects and advantages of the present invention will become apparent from the following description, taken in conjunction with the accompanying drawings, illustrating by way of example the principles of the invention.
- The invention, together with objects and advantages thereof, may best be understood by reference to the following description of the presently preferred embodiments together with the accompanying drawings in which:
- FIG. 1 is a cross-sectional view of a compressor according to a first embodiment of the present invention;
- FIG. 2 is a front view of a lug plate of the compressor of FIG. 1;
- FIG. 3 is a cross-sectional view showing a modification of a swash plate;
- FIG. 4 is a cross-sectional view of a compressor according to a second embodiment of the present invention;
- FIG. 5 is a partial cross-sectional view of a modification of a lug plate; and
- FIG. 6 is front view of the lug plate of FIG. 5.
- A
variable displacement compressor 100, which is used in a vehicle air-conditioner, according to a first embodiment of the present invention will now be discussed with reference to FIGS. 1 and 2. As viewed in FIG. 1, the left side is defined as the front side, and the right side is defined as the rear side. - As shown in FIG. 1, the
compressor 100 includes acylinder block 11, afront housing 12, which is coupled to the front end of the cylinder block, and arear housing 14, which is coupled to the rear end of thecylinder block 11 with avalve plate 13 arranged in between. Thecylinder block 11, thefront housing 12, thevalve plate 13, and therear housing 14 define a housing of thecompressor 100. - A
crank chamber 15 is defined in thecylinder block 11 and thefront housing 12. Further, thecylinder block 11 and thefront housing 12 rotatably support arotary drive shaft 16, which extends through thecrank chamber 15. Apulley 17 is connected to the front end of therotary drive shaft 16, which projects out of thefront housing 12. A vehicle engine E drives therotary drive shaft 16 by means of abelt 18, which is connected to thepulley 17. - A disk-
like lug plate 19 is connected to therotary drive shaft 16 by means of a friction damper, orcylindrical rubber damper 19A, in thecrank chamber 15. - A
swash plate 20 is accommodated in thecrank chamber 15. Theswash plate 20 is connected to thelug plate 19, or rotating body, by means of ahinge mechanism 21. By the connection between theswash plate 20 and thelug plate 19, and the support of the drive shaft, theswash plate 20 rotates integrally with therotary drive shaft 16. Further, theswash plate 20 is supported so that it slides along therotary drive shaft 16 and inclines relative to therotary drive shaft 16. - A
ring 22, which is fixed to therotary drive shaft 16, and aspring 23, which is arranged between thering 22 and theswash plate 20, determines the minimum inclination of theswash plate 20. The inclination of theswash plate 20 refers to the angle of theswash plate 20 relative to a hypothetical plane that is perpendicular to the axis of therotary drive shaft 16. The minimum inclination is the angle of theswash plate 20 when it is closest to the hypothetical plane. - A plurality of cylinder bores24 (only one shown in FIG. 1) extend parallel to the axis of the
rotary drive shaft 16 in thecylinder block 11. A single-headed piston 25 reciprocates in each cylinder bore 24. Thepiston 25, the cylinder bore 24, and thevalve plate 13 define a compression chamber. The volume of the compression chamber varies in accordance with the position of thepiston 25. Eachpiston 25 is connected to the peripheral portion of theswash plate 20 by means ofshoes 26. Accordingly, the rotation of therotary drive shaft 16, or the rotation of theinclined swash plate 20, is converted to the linear reciprocation of thepistons 25. - The cylinder block11 (cylinder bores 24), the
rotary drive shaft 16, thelug plate 19, theswash plate 20, thehinge mechanism 21, thepiston 25, and theshoes 26 form a variable displacement piston compression mechanism. - A
suction chamber 27 and adischarge chamber 28 are defined in therear housing 14. Thevalve plate 13 closes the front sides of thesuction chamber 27 and thedischarge chamber 28. When eachpiston 25 moves from its top dead center position to its bottom dead center position, refrigerant gas is drawn into the associated cylinder bore 24 (compression chambers) from thesuction chamber 27 through asuction port 29 and asuction valve 30, which are formed in thevalve plate 13. When thepiston 25 moves from the bottom dead center position to the top dead center position, the low-pressure refrigerant gas in thecylinder bore 24 is compressed to a predetermined pressure and released into thedischarge chamber 28 through adischarge port 31 and adischarge valve 32, which are formed in thevalve plate 13. - The
discharge chamber 28 is connected to thesuction chamber 27 through an external refrigerant circuit (not shown). The refrigerant is discharged from thedischarge chamber 28 and sent into the external refrigerant circuit. After exchanging heat in the external refrigerant circuit, the refrigerant is returned to thesuction chamber 27 from the external refrigerant circuit. - A
bleeding passage 33, which connects thecrank chamber 15 and thesuction chamber 27, and agas supply passage 34, which connects thedischarge chamber 28 and thecrank chamber 15, are formed in the housing. Acontrol valve 35, which adjusts the opening degree of thegas supply passage 34, is arranged in thegas supply passage 34. - By adjusting the opening degree of the
gas supply passage 34, thecontrol valve 35 changes the balance between the amount of refrigerant gas drawn into thecrank chamber 15 and the amount of refrigerant gas discharged from thecrank chamber 15. In other words, thecontrol valve 35 determines the pressure of the crank chamber 15 (crank pressure Pc) by adjusting the balance between the amount of high-pressure refrigerant gas sent into thecrank chamber 15 from thedischarge chamber 28 and the amount of refrigerant gas sent out of thecrank chamber 15 to thesuction chamber 27 through thebleeding passage 33. The difference between the crank pressure Pc and the pressure of the compression chambers, which are the pressures acting on the ends of thepistons 25, alters the inclination of theswash plate 20. This changes the stroke of thepistons 25 and varies the displacement of the compressor. - A lubricant oil mist, which is suspended in the refrigerant gas, lubricates moving parts in the
crank chamber 15. - FIG. 2 is a front view of the
lug plate 19. Acover 44 is removed from thelug plate 19 in the state of FIG. 2. Thelug plate 19 has anaxis 19×, which coincides with the axis of therotary drive shaft 16. - As shown in FIGS. 1 and 2, six equally spaced guides, or receptacles41 (only two shown in FIG. 1), are arranged in the
lug plate 19 about theaxis 19× in the circumferential direction. A mass body, or cylindrical rigid roller (cylindrical member) 43, is retained in eachreceptacle 41. Eachreceptacle 41 has a circumferential surface (guide surface) 42, which guides the rolling of the associatedroller 43. More specifically, eachreceptacle 41 is a cylindrical bore having anaxis 41×, which is separated from theaxis 19× of thelug plate 19 by a predetermined distance R1. The radius of the cylindrical bore is r1. Thus, the radius of curvature of eachguide surface 42 is equal to radius R1. - The mass of each
roller 43 is represented by m1. Further, eachroller 43 is movable along theguide surface 42 of the associatedreceptacle 41. More specifically, the diameter d1 of eachroller 43 is smaller than the diameter 2r1 of eachreceptacle 41, and the length of eachroller 43 in the axial direction is slightly less than the depth of each receptacle 41 (the depth in the axial direction of the lug plate 19). Theannular cover 44 is attached to the front end of thelug plate 19. Thecover 44 prevents therollers 43 from falling out of theguide receptacles 41. Thecover 44 also functions as a race of athrust bearing 45 and restricts forward axial movement of thelug plate 19. - When the engine E drives the
compressor 100, that is, when therotary drive shaft 16 is rotating, centrifugal force causes therollers 43 to contact the guide surfaces 42. In this state, when rotational vibrations of thelug plate 19 results in torque fluctuation, therollers 43 start to move back and forth (swing) along theguide surface 42 of the associatedreceptacle 41. In other words, each roller 43 (i.e., the center of gravity of each roller 43) starts a pendulum movement about theaxis 41× of thereceptacle 41. Accordingly, eachroller 43 functions as a centrifugal pendulum when thecompressor 100 is driven. In the first embodiment, the dimension and mass of eachroller 43 and the position where eachroller 43 is arranged on the lug plate 19 (i.e., the position and dimension of each receptacle 41) is set so that the pendulum movement of eachroller 43 suppresses torque fluctuation. - The dimension and mass of each
roller 43 and the position of eachroller 43 on thelug plate 19 will now be discussed. - The centrifugal pendulum movement of each
roller 43 suppresses torque fluctuations having a frequency that is equal to the inherent frequency of theroller 43. It is thus preferred that the dimension, mass, and position of theroller 43 be set so that the inherent frequency of theroller 43 be equal to the frequency of the torque fluctuation peak. In this case, vibrations at the torque fluctuation peak are reduced. This effectively reduces the influence of torque fluctuations. The torque fluctuation peak refers to the peak of the fluctuating amount of torque, that is, the rotation order component. - The vibrations of the torque fluctuation and the inherent vibrations of the
rollers 43 are proportional to the angular velocity ω1 of therotary drive shaft 16, which is related with the rotating speed of therotary drive shaft 16. The torque fluctuation is formed from various types of peaks that appear periodically. A first peak, in which the torque fluctuation is maximum, appears every predetermined first cycle. The frequency of the first peak is represented by (ω1/2πn)·N. In the representation, (ω1/2π) represents the rotation of therotary drive shaft 16 per unit time, and N represents the number of cylinder bores 24. The nth peak of the nth largest torque fluctuation appears at a cycle that differs from the predetermined first cycle. The frequency of such cycle is represented by n·(ω1/2π)·N. It has been confirmed through experiments that among the torque fluctuation peaks, the frequency of the nth (n being a natural number) peak has a tendency to have the same value as product n·(ω1/2π)·N. - The inherent vibration of the
roller 43 is calculated from the product of the rotation of therotary drive shaft 16 per unit time (ω1/2π) and the square root of ratio R/r. R represents the distance between the axis of thelug plate 19 and thecenter axis 41× of the pendulum movement of theroller 43, and r represents the distance between thecenter axis 41× of the pendulum movement of theroller 43 and the center of gravity g1 of theroller 43. - Accordingly, when the square root of the ratio R/r and the product n·N are equal, the inherent frequency of the
roller 43 coincides with the nth largest torque fluctuation peak. This suppresses the torque fluctuation of the vibrations at the nth largest peak. - To effectively reduce torque fluctuation with the pendulum movement of the
roller 43, the torque T about theaxis 19× of thelug plate 19 that acts on theroller 43 must be equalized with the fluctuating width of the torque fluctuation. The value of the torque T when the frequency at the torque fluctuation peak coincides with the inherent frequency of therollers 43 is calculated from the next equation. - [Equation 1]
- T=m·(ω a)2·(R+r)·R·φ
- In the equation, m is the total mass of every roller43 (m=6·m1), and ωa is the average angular velocity of the
roller 43 performing the pendulum movement at a minim swing angle φ. - In the first embodiment, the mass m of the roller is maximized to decrease the values of R, r, and φ. This enables the torque T to be increased, while preventing the
lug plate 19 from being enlarged. - In the first embodiment, the
axis 41× of eachreceptacle 41 coincides with the center of the pendulum movement of the associatedroller 43. In other words, the center of the pendulum movement of eachroller 43 is located along the associatedaxis 41×. Accordingly, the distance R1 between theaxis 41× and theaxis 19× of thelug plate 19 corresponds to R in equation 1. - The distance between the center of pendulum movement of the
roller 43, or theaxis 41× of thereceptacle 41, and the center of gravity g1 of theroller 43 is equal to a value obtained by subtracting half the diameter d1 of theroller 43 from the radius r1 of thereceptacle 41. Accordingly, the difference {r1−(d1/2)} corresponds to r in equation 1. - In the first embodiment, to suppress the maximum peak of the torque fluctuation, R1, r1, and d1 are set so that the square root of ratio R1/{r1−(d1/2)}, which corresponds with the square root of the ratio R/r, is equalized with N (the value of n·N when n=1 is satisfied).
- When various values related with the pendulum movement are set, the
roller 43 is considered to be a particle in which the mass of theroller 43 concentrates at the center of gravity g1. - The operation of the
compressor 100 will now be discussed. - When the power of the engine E is transmitted to the
rotary drive shaft 16 by means of thepulley 17, theswash plate 20 rotates with therotary drive shaft 16. The rotation of theswash plate 20 reciprocates thepistons 25 with a stroke corresponding to the inclination of theswash plate 20. The movement of thepistons 25 results in the associated cylinder bores 24 repetitively drawing in, compressing, and discharging refrigerant. - When the opening degree of the
control valve 35 decreases, the amount of high pressure refrigerant gas supplied to the crankchamber 15 via thegas supply passage 34 from thedischarge chamber 28 decreases. This decreases the crank chamber pressure Pc, increases the inclination of theswash plate 20, and increases the displacement of thecompressor 100. When the opening degree of thecontrol valve 35 increases, the amount of high pressure refrigerant gas supplied to the crankchamber 15 via thegas supply passage 34 from thedischarge chamber 28 increases. This increases the crank chamber pressure Pc, decreases the inclination of theswash plate 20, and decreases the displacement of thecompressor 100. - When the
rotary drive shaft 16 rotates, the compression reaction of the refrigerant and the reaction resulting from the reciprocation of thepistons 25 are transmitted to thelug plate 19 by theswash plate 20 and thehinge mechanism 21. This produces rotational vibrations in thelug plate 19. The rotational vibrations cause torque fluctuations. The torque fluctuation produces resonance in thecompressor 100 and between an external rotating mechanism (e.g., the engine E or an auxiliary device), which is connected to thepulley 17 by thebelt 18, and thecompressor 100. - When the torque fluctuates, each
roller 43 starts the pendulum movement. Due to the pendulum movement, the torque acting about theaxis 19× of thelug plate 19 functions to suppress the torque fluctuation. The inherent vibrations of theroller 43 are set to be equal to the vibrations at the highest peak of the torque fluctuation. This suppresses the vibrations at the highest peak of the torque fluctuation and, as a whole, effectively reduces torque fluctuations of thelug plate 19. - The
lug plate 19 is connected to therotary drive shaft 16 by arubber damper 19A. The torque fluctuation transmitted from thelug plate 19 to therotary drive shaft 16 is further reduced by therubber damper 19A. As a result, resonance caused by torque fluctuations is effectively suppressed. - The
rubber damper 19A effectively reduces relatively high frequency torque fluctuations. The pendulum movement of therollers 43 effectively reduces relatively low frequency torque fluctuations. - The first embodiment has the advantages described below.
- (1) The
rollers 43 are attached to thelug plate 19. Eachroller 43 performs a pendulum movement about a point (41×), which is separated from theaxis 19× of thelug plate 19 by the predetermined distance R1. The pendulum movement of eachroller 43 suppresses resonance produced in thecompressor 100 and resonance produced between thecompressor 100 and a rotary mechanism, which is connected to thecompressor 100 by thebelt 18. - (2) The
rollers 43 are accommodated in the housing. Thus, rotating members located on the outer side of the housing, such as thepulley 17, may easily be reduced in size. Further, the noise produced when contact occurs between thereceptacles 41, thecover 44, and therollers 43 is absorbed in the housing. Thus, the noise level of thecompressor 100 is relatively low. Further, therollers 43 are not exposed to the environment outside the housing. Thus, abnormalities resulting from rusting of therollers 43 or dust collecting on therollers 43 do not occur. Accordingly, resonance is reduced and thecompressor 100 has improved durability and weather resistance. - (3) The
rollers 43 are arranged in thecrank chamber 15. Thus, therollers 43 are lubricated by the oil mist, which lubricates the compression mechanism. - (4) The
rollers 43 have a round cross-section and roll along the associated curved guide surfaces 42, which are formed in thelug plate 19. Since therollers 43 easily perform the pendulum movement along the associated guide surfaces 42, vibrations of thecompressor 100 and resonance produced between the rotating mechanism and the compressor is suppressed. - (5) The
rubber damper 19A is arranged between thelug plate 19 and therotary drive shaft 16. Thus, in addition to the damper effect of therollers 43, the damper effect of therubber dampers 19A is also obtained. This effectively suppresses resonance. - (6) The
rollers 43 are arranged in thelug plate 19, which inclinably supports theswash plate 20. Thus, an additional rotating body does not have to be provided for therollers 43. Accordingly, resonance is suppressed without enlarging thecompressor 100. - A fixed
displacement compressor 200 according to a second embodiment of the present invention will now be discussed. - As shown in FIG. 4, the
compressor 200 has twocylinder blocks 51, which are connected to each other. Thefront housing 52 is connected to the front end of thefront cylinder block 51 with avalve plate 54 arranged in between. Arear housing 53 is connected to the rear end of therear cylinder block 51 with avalve plate 54 arranged in between. - Bolt holes55 extend through the
front housing 52 and the two cylinder blocks 51. Abolt 56, which has a threadedportion 56A on its distal end, is inserted through eachbolt hole 55 to screw the threadedportion 56A into a threadedhole 55A. Thebolt 56 fastens thefront housing 52 and therear housing 53 to the cylinder blocks 51. Thecylinder block 51, thefront housing 52, and therear housing 53 form a housing of thecompressor 200. - A
rotary drive shaft 57 is rotatably supported in the cylinder blocks 51 and thefront housing 52 by a pair ofradial bearings 51A. The front end of therotary drive shaft 57 projects outward from thefront housing 52 through acenter hole 52A, which is formed in thefront housing 52. The front end of therotary drive shaft 57 is connected to a power transmission mechanism (not shown). Therotary drive shaft 57 is driven by an external drive source, such as a vehicle engine, by means of the power transmission mechanism. - A
lip seal assembly 52B, which prevents the leakage of refrigerant gas, is attached to thefront housing 52 to seal the space between therotary drive shaft 57 and the wall of thecenter hole 52A. A plurality of (an N number of) equally spaced cylinder bores 51B extend parallel to therotary drive shaft 57 through the two cylinder blocks 51. A double-headedpiston 59 reciprocates in each cylinder bore 51B.Compression chambers 51C are defined between the end surfaces of thepistons 59, thevalve plates 54, and the cylinder bores 51B. - A
crank chamber 58 is connected to an external refrigerant circuit (not shown). Thecrank chamber 58 is supplied with relatively low refrigerant gas from the external refrigerant circuit. Thus, thecrank chamber 58 serves as part of a refrigerant passage in the housing. - A
swash plate 60, which has asleeve 60A and adisk 60B, are accommodated in thecrank chamber 58. Thesleeve 60A is fitted on therotary drive shaft 57. Thedisk 60B extends radially from thesleeve 60A. The peripheral portion of thedisk 60B is connected to the middle portion of eachpiston 59 byshoes 61. - Two
thrust bearings 62 are arranged between the cylinder blocks 51 and the front and rear sides of thesleeve 60A. The twothrust bearings 62 rotatably hold theswash plate 60 in the two cylinder blocks 51. Theswash plate 60 converts the rotation of therotary drive shaft 57 to the reciprocation of thepistons 59. The angle between theswash plate 60 and therotary drive shaft 57 is fixed. Thus, the stroke of thepistons 59 is fixed. - The
shoes 61 and theswash plate 60 form a crank mechanism. The crank mechanism, the cylinder blocks 51 (cylinder bores 51B), thepistons 59, and therotary drive shaft 57 form a piston compression mechanism. -
Suction chambers 63 are defined in the front andrear housings suction chamber 63 is connected to the bolt holes 55 through a communication hole (not shown). Accordingly, thesuction chambers 63 are connected to the crankchamber 58 through the bolt holes 55.Discharge chambers 64 are defined at the inner sides of thesuction chambers 63 in the front andrear housings discharge chamber 64 is connected to an external refrigerant circuit. - Each
valve plate 54 includes a plurality ofsuction ports 65, which are formed in correspondence with the associatedsuction chambers 63, and a plurality ofsuction valves 66, which open and close the associatedsuction ports 65. When eachpiston 59 moves from its top dead center position to its bottom dead center position in the associatedcylinder bore 51B, the correspondingsuction valve 66 opens to draw refrigerant gas into thecompression chamber 51C from the correspondingsuction chamber 63. - Further, each
valve plate 54 includes a plurality ofdischarge ports 67, which are formed in correspondence with the associateddischarge chambers 64, and a plurality ofdischarge valves 68, which open and close the associateddischarge ports 67. When eachpiston 59 moves from the bottom dead center position to the top dead center position in the associatedcylinder bore 51B, and the refrigerant gas in the correspondingcompression chamber 51C is compressed to a predetermined pressure, the correspondingdischarge valve 68 opens to discharge refrigerant into thecorresponding discharge chamber 64. - In the second embodiment, the
crank chamber 58, the bolt holes 55, thesuction chambers 63, thesuction ports 65, thecompression chambers 51C, thedischarge ports 67, and thedischarge chambers 64 form the refrigerant passage in the housing. Components in the refrigerant circuit in the housing are lubricated by oil mist, which circulates with refrigerant gas in the passage. - The
disk 60B of theswash plate 60 has a plurality of guides, orreceptacles 60C (only two shown in FIG. 4). A cylindrical mass body, orroller 69, is accommodated in eachreceptacle 60C. Acover 60D is attached to theswash plate 60 to close the opening of thereceptacles 60C. - Each
roller 69 rolls along aguide surface 60E of thereceptacles 60C. When viewed from a plane perpendicular to the axis of the swash plate 60 (i.e., axis of the rotary drive shaft 57), theguide surface 60E is arcuate. - When the
rotary drive shaft 57 rotates, the compression reaction of the refrigerant gas and the reaction resulting from the reciprocation of thepistons 59 vibrate theswash plate 60. The vibration of theswash plate 60 moves each roller 69 (or the center of gravity of each roller 69) outward by a predetermined distance from the axis of theswash plate 60. Then, theroller 60 performs a pendulum movement about a center point that is separated from the axis of theswash plate 60 by a predetermined distance. - In the same manner as in the first embodiment, in the second embodiment, R and r are set so that the square root of ratio R/r is equalized with N (the value of n·N when n=1 is satisfied). This efficiently suppresses the maximum peak of torque fluctuation, which results from the rotational vibrations of the
compressor 200. R represent the distance between the axis of theswash plate 60 and the center point of the pendulum movement of eachroller 69, and r represents the distance between the center point of the pendulum movement of eachroller 69 and the center of gravity of theroller 69. - In addition to advantages (1) to (4) and (6) of the first embodiment, the second embodiment has the advantages described below.
- (7) The inclination between the
swash plate 60 and therotary drive shaft 57 is fixed. Thus, the position of the center point of the pendulum movement of eachroller 69 relative to theswash plate 60 does not change. Accordingly, the efficiency for suppressing resonance with therollers 69 is stably maintained. - The first and second embodiments may be modified as described below.
- The
lug plate 19 of the first embodiment may be directly connected to therotary drive shaft 16 without therubber damper 19A. - A spring, such as a metal plate spring, may be used in lieu of the
rubber damper 19A in the first embodiment. In such a case, thelug plate 19 has a recess formed in a surface corresponding to the cylindrical surface of therotary drive shaft 16, and therotary drive shaft 16 has a recess formed in a surface corresponding to thelug plate 19. One end of a square plate spring is received in the recess of thelug plate 19. The other end of the plate spring is received in the recess of therotary drive shaft 16. This connects thelug plate 19 and therotary drive shaft 16. - In the first embodiment, the
cover 44 is also used as the race of thethrust bearing 45. However, thecover 44 does not have to be used as a race. In such a case, a member that differs from the race of thethrust bearing 45 preventsrollers 43 from falling out of thereceptacles 41. - In the
compressor 100 of the first embodiment, theswash plate 20 rotates integrally with therotary drive shaft 16. However, the present invention may also be applied to a wobble plate compressor in which a cam plate, or a wobble plate, rotates relative to a rotary drive shaft. - The present invention may be applied to a fixed displacement compressor having pistons with a fixed stroke in lieu of the
compressor 100 of the first embodiment. - The
swash plate 60 of the second embodiment may be modified as shown in FIG. 3. More specifically, theswash plate 60 of FIG. 3 has cylindrical bores, the axes of which are parallel to the axis of theswash plate 60. In this case, aroller 69 rolls along aguide surface 60E of each cylinder bore to perform a pendulum movement. When theswash plate 60 is rotating, the movement of theroller 69 toward therotary drive shaft 57 is restricted. This effectively suppresses resonance. FIG. 3 shows theswash plate 60 in a state before it is attached to therotary drive shaft 57. - The
swash plate 60 of the second embodiment may be connected to therotary drive shaft 57 by means of a friction damper. In such a case, the damper effect obtained by the cooperation between therollers 69 and the friction damper effectively suppresses resonance. - Instead of the
rollers rotating bodies lug plate 19 hasreceptacles 82, each of which accommodates a mass body, or apendulum 81. Eachreceptacle 82 has ainner surface 82A to which apivot pin 83 is fixed parallel to the axis of thelug plate 19. Thepivot pin 83 pivotally supports one of thependulums 81. Thependulum 81 performs the pendulum movement about thepivot pin 83 in accordance with the rotational vibrations produced when therotary drive shaft 16 rotates. - In the same manner as the first and second embodiments, it is preferred that R and r be set so that the square root of ratio R/r be equalized with N (the value of n·N when n=1 is satisfied) to suppress the maximum peak of torque fluctuation, which is caused by the rotational vibrations. R represents the distance between the axis of the
lug plate 19 and eachpivot pin 83, and r represents the distance between thepivot pin 83 and the center of gravity of eachpendulum 81. - As shown in FIGS. 5 and 6, each
pendulum 81 is supported by the associatedpivot pin 83, which is fixed to thelug plate 19. However, thepivot pin 83 may be fixed to thependulum 81, and thepivot pin 83 may be inserted in a hole formed in thelug plate 19. Further, as shown in FIGS. 5 and 6, thependulums 81 are arranged on thelug plate 19. However, thependulums 81 may be arranged on theswash plate 60 of the second embodiment. - The present invention may be applied to a member other than the
lug plate 19 or theswash plate 60 as long as the member is a rotating body connected to a rotary drive shaft that is arranged in a housing of a compressor. - The
mass bodies - The square root of ratio R/r does not have to be set so that it is equalized with the value of product n·N, or N, when n=1 is satisfied. For example, the square root of the ratio R/r may be set so that it is equalized with the value of product n·N when n is a natural number of two or greater (e.g., 2 or 3).
- The number of mass bodies (e.g., the
rollers - The value corresponding to the square root of the ratio R/r may differ between each mass body (
rollers - A plurality of products n·N (e.g., 1·N, 2·N, 3·N) may correspond to a plurality of the square roots of R/r, respectively. In such a case, more than two peaks of the torque fluctuation starting from the largest one (in this case, three) are suppressed. This further improves the resonance suppressing effect.
- It is preferred that the above calculations be performed by considering the mass body as an object having a volume and not as a particle. For example, with regard to the pendulum movement of the
cylindrical rollers 43, the ratio R/r may be replaced by ratio 2R/3r. This would include the inertial weight of the mass body. In this case, torque T is obtained from the next equation. In the equation, the vibrations at the peak of the torque fluctuation coincide with the inherent vibrations of therollers 43. - [Equation 2]
- T=(3/2)·m·(ωa)2·(R+r)·R·φ
- Further, when the mass body, which rolls along the guide surface, is spherical, ratio R/r is replaced by ratio 5R/7r to take the inertial weight into consideration. Further, the level of the torque T when the vibrations at the peak of the torque fluctuation in this case matches the inherent vibrations of the spherical mass body is obtained from the next equation.
- [Equation 3]
- T=(7/5)·m·(ωa)2·(R+r)·R·φ
- When the mass body is neither cylindrical nor spherical, by making various settings taking into consideration the inertial weight that corresponds to the shape of the mass body, resonance may be suppressed more effectively.
- Instead of the
piston compressors - Instead of the
compressors rotary drive shafts - The axis of the pendulum movement of the mass body does not have to be parallel to the axis of the rotating body. For example, as long as the maximum amount of the torque fluctuation is within a desirable range, the axis of the pendulum movement may be inclined relative to the axis of the rotating body.
- It should be apparent to those skilled in the art that the present invention may be embodied in many other specific forms without departing from the spirit or scope of the invention. Therefore, the present examples and embodiments are to be considered as illustrative and not restrictive, and the invention is not to be limited to the details given herein, but may be modified within the scope and equivalence of the appended claims.
Claims (17)
1. A compressor including a housing, a rotary drive shaft rotatably supported by the housing, and a compression mechanism accommodated in the housing, the compressor comprising:
a rotating body connected to the rotary drive shaft and arranged in the housing; and
a mass body supported by the rotating body at a position radially separated from an axis of the rotating body by a predetermined distance, wherein the mass body is supported in a manner permitting pendulum movement.
2. The compressor according to claim 1 , wherein the mass body is arranged in the housing.
3. The compressor according to claim 1 , wherein the compression mechanism includes a piston, which reciprocates when the rotary drive shaft rotates, and a swash plate, which converts the rotation of the rotary drive shaft to the reciprocation of the piston, and wherein the compressor further comprises a crank chamber, which accommodates the compression mechanism, and the mass body is arranged in the crank chamber.
4. The compressor according to claim 1 , wherein the rotating body has a guide, wherein the center of the guide is separated from the axis of the rotating body by the predetermined distance, wherein the guide has a curved guide surface, and wherein the mass body is a cylindrical member accommodated in the guide and rolls along the guide surface.
5. The compressor according to claim 4 , wherein the guide is one of a plurality of guides, wherein the guides are equally spaced in the circumferential direction of the rotating body.
6. The compressor according to claim 1 , further comprising a friction damper arranged between the rotating body and the rotary drive shaft.
7. The compressor according to claim 1 , wherein the compression mechanism is a variable displacement piston compression mechanism including a piston, which reciprocates when the rotary drive shaft rotates, and a swash plate, which converts the rotation of the rotary drive shaft to the reciprocation of the piston, wherein the rotating body is a lug plate, which supports the swash plate in a manner so that the swash plate inclines at an angle relative to the rotary drive shaft, wherein the angle determines the displacement of the compressor, and wherein the angle is altered to change said displacement.
8. The compressor according to claim 7 , wherein the guide is a recess formed in the lug plate.
9. The compressor according to claim 8 , wherein the recess is closed by a cover.
10. The compressor according to claim 1 , wherein the compression mechanism is a fixed displacement piston compression mechanism including a piston, which reciprocates when the rotary drive shaft rotates, and a swash plate, which converts the rotation of the rotary drive shaft to the reciprocation of the piston, and wherein the rotating body is the swash plate.
11. The compressor according to claim 10 , wherein the guide is a recess formed in the swash plate.
12. The compressor according to claim 11 , wherein the recess is closed by a cover.
13. A compressor including a housing, a rotary drive shaft rotatably supported by the housing, and a compression mechanism accommodated in the housing, the compressor comprising:
a rotating body arranged in the housing and rotated integrally with the rotary drive shaft, wherein the rotating body includes a plurality of receptacles equally spaced in the circumferential direction of the rotating body, wherein the centers of the receptacles are separated from the axis of the rotating body by a first predetermined distance; and
a plurality of mass bodies respectively accommodated in the plurality of receptacles, wherein the mass bodies each perform a pendulum movement in the associated receptacle when the rotary drive shaft rotates.
14. The compressor according to claim 13 , wherein each of the mass bodies swings about an axis that is separated from the axis of the rotating body by a second predetermined distance.
15. The compressor according to claim 13 , wherein, for each mass bodies, the axis of pendulum movement is inclined relative to the axis of the rotating body.
16. The compressor according to claim 13 , wherein each of the mass bodies is a cylindrical rigid body roller, and each of the receptacles has a curved guide surface that contacts the associated cylindrical rigid body roller.
17. The compressor according to claim 13 , further comprising a plurality of pins, each connecting one of the mass bodies to the rotating body, wherein the mass bodies swing about the associated pins.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2001196631A JP2003013856A (en) | 2001-06-28 | 2001-06-28 | Compressor |
JP2001-196631 | 2001-06-28 |
Publications (1)
Publication Number | Publication Date |
---|---|
US20030002991A1 true US20030002991A1 (en) | 2003-01-02 |
Family
ID=19034402
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/183,719 Abandoned US20030002991A1 (en) | 2001-06-28 | 2002-06-27 | Compressor |
Country Status (3)
Country | Link |
---|---|
US (1) | US20030002991A1 (en) |
EP (1) | EP1270943A3 (en) |
JP (1) | JP2003013856A (en) |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20020189393A1 (en) * | 2001-06-14 | 2002-12-19 | Yasuo Tabuchi | Torque transmission apparatus |
US20080298980A1 (en) * | 2007-06-01 | 2008-12-04 | Halla Climate Control Corp. | Compressor |
US20120304809A1 (en) * | 2010-02-19 | 2012-12-06 | Hiroaki Yamamoto | Balancer |
US20150087455A1 (en) * | 2013-09-25 | 2015-03-26 | Hyundai Motor Company | Alternator pulley, and mounting structure of alternator pulley and alternator for vehicle |
US20160223067A1 (en) * | 2015-01-30 | 2016-08-04 | Hyundai Motor Company | Device for Noise Vibration Reduction of Alternator's Pulley |
US10711395B2 (en) | 2015-07-24 | 2020-07-14 | The Procter & Gamble Company | Textured fibrous structures |
US11148147B2 (en) | 2015-06-12 | 2021-10-19 | The Procter & Gamble Company | Discretizer and method of using same |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1751429B1 (en) * | 2004-05-17 | 2008-03-12 | Koninklijke Philips Electronics N.V. | Reciprocating pump with reduced noise level |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4762468A (en) * | 1986-08-25 | 1988-08-09 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Shoe-and-socket joint in a swash plate type compressor |
US5737997A (en) * | 1995-08-21 | 1998-04-14 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Cam plate supporting structure in a cam plate type compressor |
US5785503A (en) * | 1995-11-24 | 1998-07-28 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Variable displacement compressor |
US5784950A (en) * | 1996-03-26 | 1998-07-28 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Single headed swash plate type compressor having a piston with an oil communication hole on a side of the piston remote from the cylinder bore and crank chamber |
US20020146326A1 (en) * | 2001-03-14 | 2002-10-10 | Masahiro Kawaguchi | Compressor and pulley for compressor |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH09317628A (en) * | 1996-05-31 | 1997-12-09 | Toyota Autom Loom Works Ltd | Compressor |
JP3832012B2 (en) * | 1997-03-31 | 2006-10-11 | 株式会社豊田自動織機 | Variable capacity compressor |
JPH11159453A (en) * | 1997-11-28 | 1999-06-15 | Toyota Autom Loom Works Ltd | Torsional resonance dampting structure of driving system in compressor |
JPH11324919A (en) * | 1998-05-11 | 1999-11-26 | Toyota Autom Loom Works Ltd | Method and device for restraining resonance |
JP2000213600A (en) | 1999-01-22 | 2000-08-02 | Nok Megulastik Co Ltd | Centrifugal pendulum vibration absorber |
JP2000274489A (en) * | 1999-03-26 | 2000-10-03 | Nok Megulastik Co Ltd | Dynamic damper |
-
2001
- 2001-06-28 JP JP2001196631A patent/JP2003013856A/en active Pending
-
2002
- 2002-06-27 EP EP02014347A patent/EP1270943A3/en not_active Withdrawn
- 2002-06-27 US US10/183,719 patent/US20030002991A1/en not_active Abandoned
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4762468A (en) * | 1986-08-25 | 1988-08-09 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Shoe-and-socket joint in a swash plate type compressor |
US5737997A (en) * | 1995-08-21 | 1998-04-14 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Cam plate supporting structure in a cam plate type compressor |
US5785503A (en) * | 1995-11-24 | 1998-07-28 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Variable displacement compressor |
US5784950A (en) * | 1996-03-26 | 1998-07-28 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Single headed swash plate type compressor having a piston with an oil communication hole on a side of the piston remote from the cylinder bore and crank chamber |
US20020146326A1 (en) * | 2001-03-14 | 2002-10-10 | Masahiro Kawaguchi | Compressor and pulley for compressor |
Cited By (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20020189393A1 (en) * | 2001-06-14 | 2002-12-19 | Yasuo Tabuchi | Torque transmission apparatus |
US6705181B2 (en) * | 2001-06-14 | 2004-03-16 | Nippon Soken, Inc. | Torque transmission apparatus |
US20080298980A1 (en) * | 2007-06-01 | 2008-12-04 | Halla Climate Control Corp. | Compressor |
US9989120B2 (en) | 2010-02-19 | 2018-06-05 | Hiroaki Yamamoto | Balancer |
US9206879B2 (en) * | 2010-02-19 | 2015-12-08 | Hiroaki Yamamoto | Balancer |
US20120304809A1 (en) * | 2010-02-19 | 2012-12-06 | Hiroaki Yamamoto | Balancer |
US20150087455A1 (en) * | 2013-09-25 | 2015-03-26 | Hyundai Motor Company | Alternator pulley, and mounting structure of alternator pulley and alternator for vehicle |
US9291252B2 (en) * | 2013-09-25 | 2016-03-22 | Hyundai Motor Company | Alternator pulley, and mounting structure of alternator pulley and alternator for vehicle |
US20160223067A1 (en) * | 2015-01-30 | 2016-08-04 | Hyundai Motor Company | Device for Noise Vibration Reduction of Alternator's Pulley |
US9784358B2 (en) * | 2015-01-30 | 2017-10-10 | Hyundai Motor Company | Device for noise vibration reduction of alternator's pulley |
US11148147B2 (en) | 2015-06-12 | 2021-10-19 | The Procter & Gamble Company | Discretizer and method of using same |
US10711395B2 (en) | 2015-07-24 | 2020-07-14 | The Procter & Gamble Company | Textured fibrous structures |
US11174590B2 (en) | 2015-07-24 | 2021-11-16 | The Procter & Gamble Company | Textured fibrous structures |
US11732406B2 (en) | 2015-07-24 | 2023-08-22 | The Procter & Gamble Company | Textured fibrous structures |
Also Published As
Publication number | Publication date |
---|---|
EP1270943A3 (en) | 2004-03-31 |
EP1270943A2 (en) | 2003-01-02 |
JP2003013856A (en) | 2003-01-15 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
KR102480987B1 (en) | Scroll compressor | |
US6139282A (en) | Variable capacity refrigerant compressor with an aluminum cam plate means | |
US6719537B2 (en) | Compressor and pulley for compressor | |
EP1286050A2 (en) | Rotary damper | |
US5975860A (en) | Vibration torsion system damper for a shaft of a compressor | |
KR20200112247A (en) | Scroll compressor | |
US20030000783A1 (en) | Rotary machine | |
US20030002991A1 (en) | Compressor | |
US20030000377A1 (en) | Rotor and compressor | |
US20040265144A1 (en) | Hybrid compressor | |
JP6742484B2 (en) | Scroll compressor | |
EP0919725A1 (en) | Compressor | |
KR100274969B1 (en) | Variable displacement swash plate compressor | |
JP2002340097A (en) | Rotor and compressor | |
EP0911521B1 (en) | Arrangement of lubrication fluid grooves in a rotating drive plate for a swash plate compressor | |
US20060222513A1 (en) | Swash plate type variable displacement compressor | |
KR20190033880A (en) | Swash plate type compressor | |
EP1342920A2 (en) | Compressor balancing system | |
US20040253121A1 (en) | Rotary machine | |
KR20230098437A (en) | Scroll compressor | |
KR20220091135A (en) | Scroll compressor | |
KR20220153923A (en) | Scroll compressor | |
JP2002340143A (en) | Compressor | |
KR100715261B1 (en) | Variable displacement swash plate type compressor | |
CN113260786A (en) | Compressor |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: KABUSHIKI KAISHA TOYOTA JIDOSHOKKI, JAPAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:KAWATA, TAKESHI;KAWAGUCHI, MASAHIRO;OTA, MASAKI;AND OTHERS;REEL/FRAME:013066/0516 Effective date: 20020618 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |