CN103032325B - Screw compressor - Google Patents
Screw compressor Download PDFInfo
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- CN103032325B CN103032325B CN201210356941.XA CN201210356941A CN103032325B CN 103032325 B CN103032325 B CN 103032325B CN 201210356941 A CN201210356941 A CN 201210356941A CN 103032325 B CN103032325 B CN 103032325B
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- Prior art keywords
- drive shaft
- motor drive
- motor
- helical
- lobe compressor
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0021—Systems for the equilibration of forces acting on the pump
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/06—Silencing
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- 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
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2210/00—Fluid
- F04C2210/22—Fluid gaseous, i.e. compressible
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/40—Electric motor
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S415/00—Rotary kinetic fluid motors or pumps
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S417/00—Pumps
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Motor Or Generator Frames (AREA)
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
Abstract
A cantilever type screw compressor directly connecting a motor has a damping structure, which is inability of generating unbalanced force during rotation of a rotor shaft and directly minimizes vibration of the rotor shaft itself. The screw compressor (1) comprises a screw rotor (41); a motor shaft (7) integrally formed with the screw rotor (41) and supported by a cantilever at the screw rotor side; and a motor which rotates the motor shaft (7). The screw compressor (1) comprises a cylinder component (43) being substantially coaxial to the motor shaft (7) and inserted between a gap between a motor side end face (7a) of the motor shaft (7) and an end component (10) in a gap fit manner along the inner surface of a rotating member (5), and a weight (8) being substantially coaxial to the motor shaft (7) and inserted in the cylinder component in a gap fit. The natural vibration frequency of the cylinder component is identical to that of the rotor shaft (11).
Description
Technical field
The present invention relates to the compressor of screw.
Background technology
The helical-lobe compressor of the direct connecting structure of motor is higher than the device effciency of energy transfer via the power delivery mode of rotating band.Further, employ in the helical-lobe compressor of rotating speed control mode of converter in employing, the helical-lobe compressor of the direct connecting structure of motor becomes main flow.At this, from the object reducing costs, reduce mechanical loss, be mostly formed as the one-sided motor directly link type helical-lobe compressor that the cantilevered fashion of bearing is not set at motor drive shaft.
The helical-lobe compressor of cantilevered fashion is usually to make cal speed adopt the design of rotor-shaft system considerably beyond the mode of running rotating speed.But in the helical-lobe compressor of exciting force producing pressure fluctuation composition, sometimes when the rotation speed operation of the cal speed (rotating speed) well below armature spindle, the vibration of rotor-shaft system part becomes large.And, when the vibration that the imbalance determined by axle rotating speed causes high order composition because of rotor-shaft system to rock etc. occur significantly, sometimes, still when the rotation speed operation lower than cal speed (rotating speed), the vibration of rotor-shaft system part becomes large.
At this, as the method for vibration reducing helical-lobe compressor, there is the method controlled based on the method using the such arrangement for damping oscillations of the dynamic vibration absorber of vibration-proof rubber, the rotating speed of mode to armature spindle that become large rotary speed area to skip vibration.
But, following problem is there is: when causing the setting model of vibration-proof rubber part etc. to change because of the deterioration of rubber, the lax of installation etc. in the method for the arrangement for damping oscillations such based on dynamic vibration absorber, the resonant frequency of rotor-shaft system part changes, and can not obtain vibration-damping effect.Further, when adopting the helical-lobe compressor of rotating speed control mode using converter, only having the dynamic vibration absorber of attenuating at CF can not be corresponding with the vibration of whole rotary speed area.
On the other hand, in the method controlled with the rotating speed of mode to armature spindle skipping the large rotary speed area of vibration change, also need under secure conditions to skip the rotary speed area that vibration becomes large rotating speed periphery, sometimes real machine operating condition is counteracted.
Have nothing to do as the eigentone with helical-lobe compressor and the method (method of the vibration of whole rotary speed area can be reduced) of vibration can be reduced, there is the method such as described in patent document 1.A kind of helical-lobe compressor is recorded in patent document 1, the feature of this helical-lobe compressor is, clava is provided projectingly on motor case in the horizontal direction, and the plate (mass body) with hole is inserted this clava, this hole has larger play.According to this structure, cause plate (mass body) to carry out displacement at above-below direction because of the vibration of motor case, the clava and the plate (mass body) that are provided projectingly on motor case collide and consume vibrational energy, thus reduce the vibration of motor case.
At first technical literature
Patent document
Patent document 1: Japanese Unexamined Patent Publication 2003-343641 publication
At this, when the motor directly link type helical-lobe compressor of cantilevered fashion, when the vibration of the rotor-shaft system part of this helical-lobe compressor becomes large, the whirling vibration of armature spindle significantly becomes large, and the distance between the revolving part of motor and fixture broadens or narrows.Now, because the magnetic attraction acted between revolving part and fixture changes, therefore be not only the impact that revolving part is subject to based on magnetic attraction, fixture side is also subject to the impact based on magnetic attraction, and the motor case being provided with fixture is subject to magnetic attraction and excited and vibrate.Like this, the revolving part side being not only motor vibrates, and fixture side also vibrates, and the revolving part of motor vibrates under the state be coupled with motor case thus, sometimes makes revolving part contact with fixture along with this vibration aggravation.Consequently, fixture side is damaged and produces the state being difficult to continuous running sometimes.
As mentioned above, in the vibration minimizing method described in patent document 1, utilization is provided projectingly on the clava of motor case and inserts the vibration that this claval plate (mass body) that can carry out displacement along the vertical direction reduces " motor case ".Therefore, the vibration of revolving part side will be caused to increase because of the effect of the vibration of motor case.But, when large in the vibration of the armature spindle self of helical-lobe compressor, to be formed as the permission load such as exceeding bearing vibration, need to take some vibration countermeasures to the armature spindle self of helical-lobe compressor.In addition, when taking vibration countermeasure to armature spindle self, the mode that this vibration countermeasure must carry out acting on using the unbalanced force (out-of-balance force) when avoiding the rotation as armature spindle is discussed.
In addition, be provided projectingly on the clava of motor case and inserting in the such structure of this claval plate (mass body) that can carry out displacement along the vertical direction, need the space guaranteeing to configure clava and plate (mass body) in the outside of motor case, sometimes become the restriction of the assembling layout of compressor.Further, also become for obtaining thermally equilibrated restriction.
Summary of the invention
The present invention completes in view of above-mentioned actual conditions, its object is to provide a kind of motor directly link type helical-lobe compressor possessing the cantilevered fashion of vibration-proof structure, this vibration-proof structure is difficult to produce unbalanced force (out-of-balance force) when the rotation of armature spindle, and directly can reduce the vibration of armature spindle self.
To achieve these goals, the invention provides a kind of helical-lobe compressor, it is characterized in that, described helical-lobe compressor possesses: screw rotor; Accommodate the screw rod shell of described screw rotor; Motor drive shaft, this motor drive shaft and described screw rotor form as one structure, and in screw rotor side by cantilever support; And the motor that described motor drive shaft is rotated, described motor has: the revolving part being fixed on the periphery of described motor drive shaft; Be configured at the fixture in the outside of described revolving part; And accommodate the motor case of described revolving part and described fixture, the motor-side end face of described motor drive shaft is positioned at the position leaning on screw rotor side than the motor-side end face of described revolving part, end member is fixed with at the motor-side end face of described revolving part, this end member is coaxial with described motor drive shaft, and described helical-lobe compressor also possesses: with described motor drive shaft roughly coaxial and along described revolving part inner face and insert the cylinder element in the space be configured between the motor-side end face of described motor drive shaft and described end member in the mode of matched in clearance; And roughly coaxial and insert the vibrating body of the inner side being configured at described cylinder element in the mode of matched in clearance with described motor drive shaft, the eigentone of described cylinder element is coincide with the vibration frequency that the armature spindle be made up of described screw rotor and described motor drive shaft carries out resonating.
According to this structure, for the flexural vibrations of armature spindle, collided with vibrating body by cylinder element, the axially end of travel (such as, the motor-side end face of motor drive shaft) etc. of front and back, rubbed, vibrational energy dissipates thus, and the vibration of armature spindle reduces.And, the vibration frequency of being undertaken resonating by making the eigentone of cylinder element and armature spindle is coincide, thus when producing resonance at armature spindle, in the excited larger vibration of cylinder element part, utilize the vibration of this facilitated vibrating body, thus the vibration improved further based on collision and friction reduces performance.
In addition, cylinder element and vibrating body are configured to motor drive shaft roughly coaxial, are difficult to thus produce unbalanced force (out-of-balance force) when the rotation of armature spindle.
Invention effect
According to the present invention, be difficult to produce unbalanced force (out-of-balance force) when the rotation of armature spindle, and directly can reduce the vibration of armature spindle self.
Accompanying drawing explanation
Fig. 1 is the side generalized section of the helical-lobe compressor illustrated involved by the first embodiment of the present invention.
Fig. 2 is A portion enlarged drawing and the X-X sectional view thereof of Fig. 1.
Fig. 3 is the side generalized section of the helical-lobe compressor illustrated involved by the second embodiment of the present invention.
Fig. 4 is B portion enlarged drawing and the Y-Y sectional view thereof of Fig. 3.
Fig. 5 is the Partial enlarged side generalized section of the variation that the helical-lobe compressor shown in Fig. 1 and Fig. 2 is shown.
The explanation of Reference numeral
1: helical-lobe compressor
2: screw body portion
3: screw shaft
5: revolving part
6: fixture
7: motor drive shaft
8: weight (vibrating body)
9: bolt (bar-shaped by sliding component)
10: end member
11: armature spindle
12: screw rod shell
13: motor case
30: motor part (motor)
41: screw rotor
43: cylinder element
Detailed description of the invention
Below, be described for implementing mode of the present invention with reference to accompanying drawing.
(the first embodiment)
Fig. 1 is the side generalized section of the helical-lobe compressor 1 illustrated involved by the first embodiment of the present invention.Fig. 2 is A portion enlarged drawing (Fig. 2 (a)) and the X-X sectional view (Fig. 2 (b)) thereof of Fig. 1.
(formation of helical-lobe compressor)
As shown in Figure 1, helical-lobe compressor 1 is the helical-lobe compressor of the direct connecting structure of motor possessing screw body portion 2 and motor part 30 (motor).
(screw body portion)
Screw body portion 2 has the screw rod shell 12 of screw rotor 41 and collecting screw rotor 41.Screw rotor 41 has screw rod teeth portion 4 and coaxial and to form as one the screw shaft 3 of structure with this screw rod teeth portion 4 with screw rod teeth portion 4.Screw shaft 3 is by bearing 14 and bearing 15 double base.
Screw rod teeth portion 4 and screw shaft 3 are manufactured by machining etc. by steel.In addition, also rigid attachment (one links) can be carried out after individually manufacturing screw rod teeth portion 4 and screw shaft 3.Further, screw rotor 41 and motor drive shaft 7 described later are also manufactured and the structure that forms as one by machining etc. by steel.The armature spindle 11 of rotation is made up of screw rotor 41 and the motor drive shaft 7 of the structure that mutually forms as one.In addition, also rigid attachment (one links) can be carried out after individually manufacturing screw rotor 41 and motor drive shaft 7.As the method for rigid attachment (integrative-structure), there is flange link etc.
(motor part)
Motor part 30 (motor) is the drive source for making armature spindle 11 rotate, and has: the revolving part 5 being fixed on the periphery of motor drive shaft 7; Be configured at the fixture 6 in the outside of revolving part 5; And the motor case 13 of collecting revolving part 5 and fixture 6.Motor drive shaft 7 is coaxial and form as one structure with screw rotor 41 (screw shaft 3) with screw rotor 41 (screw shaft 3), and in screw rotor 41 side by cantilever support.Specifically, motor drive shaft 7 is by bearing 14 (and bearing 15) cantilever support of screw rotor 41 side.
The motor-side end face 7a of motor drive shaft 7 is positioned at the position leaning on screw rotor 41 side than the motor-side end face 5a of revolving part 5.Bolt (not shown) etc. is utilized to be fixed with discoideus end member 10 at the motor-side end face 5a of revolving part 5.Porose 10a is offered at the center of end member 10.End member 10 is set to motor drive shaft 7 coaxial.
(damper mechanism portion)
Space between the motor-side end face 7a and end member 10 of motor drive shaft 7 is inserted with cylinder element 43.Cylinder element 43 with motor drive shaft 7 roughly coaxial and along revolving part 5 inner face and insert in the mode of matched in clearance and be configured at revolving part 5, end member 10 and motor drive shaft 7.
The length of cylinder element 43 is less than the interval between motor-side end face 7a and end member 10.The axially-displaceable momentum of cylinder element 43 is such as about 0.5mm ~ number mm.Further, the external diameter of cylinder element 43 is less than the internal diameter of revolving part 5.The movable amount of axle orthogonal direction of cylinder element 43 is substantially equal to the chimeric size between revolving part 5 and fixture 6, such as, is about 0.02mm ~ about 0.5mm.
In addition, the motor-side end face 7a of motor drive shaft 7 and motor drive shaft 7 coaxially (pivot at motor drive shaft 7) be fixed with bolt 9.The bolt 9 being configured at the inner side of revolving part 5 is involved in the present invention bar-shaped by an example of sliding component.
As shown in Fig. 2 (a), bolt 9 comprises: be fixed on the state of the through hole 10a be formed centrally in end member 10 the motor-side end face 7a of motor drive shaft 7 by sliding axle portion 16 and be formed at by the head 17 (large-diameter portion) of the end in sliding axle portion 16.The external diameter of head 17 is than large by the diameter of axle in sliding axle portion 16.Less than the diameter of axle of motor drive shaft 7 by the diameter of axle in sliding axle portion 16.
At this, contain multiple tabular in the inner side of cylinder element 43 and be the weight 8 of ring-type, this weight 8 be formed as with the mode of matched in clearance be inserted in bolt 9 by the state in sliding axle portion 16.In the present embodiment, although be formed as six weights 8, six are not limited to.Also can be one.Weight 8 is examples for the ring bodies (vibrating body) of plate shape in the present invention.
Interval between the Thickness Ratio motor-side end face 7a of the total of six weights 8 and end member 10 is little.That is, weight 8 can moving axially along motor drive shaft 7.The axially-displaceable momentum of weight 8 is such as about 0.5mm ~ number mm.Further, the external diameter (diameter) of weight 8 is less than the internal diameter of cylinder element 43.Further, as mentioned above, due to weight 8 with the mode of matched in clearance be inserted in bolt 9 by sliding axle portion 16, therefore also can move (displacement) at the axle orthogonal direction of motor drive shaft 7.The movable amount of axle orthogonal direction of weight 8 is substantially equal to the chimeric size between revolving part 5 and fixture 6, is such as about 0.02mm ~ about 0.5mm.
At this, in Fig. 2 (a), weight 8 is illustrated as with motor drive shaft 7 coaxial.But, make weight 8 with the mode inserting bolt 9 of matched in clearance by sliding axle portion 16 in static state under, strictly speaking, the axle center being formed as weight 8 to reduce the state of the movable amount (about 0.02mm ~ 0.5mm) of the axle orthogonal direction of weight 8 than the axle center of motor drive shaft 7 to direction under vertical.Namely, in the present invention, weight 8 (vibrating body) is configured to express with motor drive shaft 7 " roughly " is coaxial, and the axle center being formed as weight 8 (vibrating body) to reduce the state of the movable amount of this axle orthogonal direction than the axle center of motor drive shaft 7 to direction under vertical.
Also be in the same manner about cylinder element 43, in the present invention, cylinder element 43 is configured to express with motor drive shaft 7 " roughly " is coaxial, and the axle center being formed as cylinder element 43 to reduce the state of the movable amount (about 0.02mm ~ 0.5mm) of this axle orthogonal direction than the axle center of motor drive shaft 7 to direction under vertical.
So, weight 8 is to be configured to motor drive shaft 7 roughly coaxial with the state that the peripheral member such as motor-side end face 7a, end member 10 of motor drive shaft 7 axially etc. is colliding.In the present embodiment, owing to using multiple weight 8, therefore multiple weight 8 is also formed as in axially collision mutually.
In addition, although be circular by the cross sectional shape in sliding axle portion 16, it must be circular for not needing, and such as, also can be quadrangle etc.The hole 8a being formed at the center of weight 8 is also identical, may not be circle but such as quadrangle etc.Be formed at the shape of the hole 8a at the center of weight 8 and coincide by the cross sectional shape in sliding axle portion 16.Further, although the cross sectional shape of head 17 is hexagon, not needing must be hexagon, also can be such as circle etc.
(eigentone of cylinder element)
At this, the eigentone of the armature spindle 11 that the eigentone of cylinder element 43 is formed with by screw rotor 41 and motor drive shaft 7 is consistent.The eigentone of armature spindle 11 consider such as to rotate integrally with armature spindle 11 parts, i.e. armature spindle 11, revolving part 5, bolt 9 and end member 10 and so on parts and obtain by calculating.The eigentone of cylinder element 43 is adjusted by selecting its length, thickness, external diameter, internal diameter and material etc.
(effect, effect)
According to helical-lobe compressor 1, for the flexural vibrations of the armature spindle 11 that the rotation of mainly screw rotor 41 causes, the end of travel (the motor-side end face 7a of motor drive shaft 7 and the end face of end member 10) of cylinder element 43, axially front and back collides with weight 8 (vibrating body), rubs, vibrational energy dissipates (dissipation based on the vibrational energy of axial impact) thus, and the vibration of armature spindle 11 reduces.That is, the weight 8 collided axially etc. moving can be utilized directly to reduce the vibration of the armature spindle 11 self of rotation.And, owing to becoming opposite side end (near end member 10) the configuration weight 8 of the cantilever support side of large part and motor drive shaft 7 in the flexural vibrations of armature spindle 11, the dissipation efficiency of the vibrational energy based on axial impact can be improved thus further.
In addition, make the eigentone of cylinder element 43 consistent with the eigentone of armature spindle 11, thus near the eigentone of armature spindle 11, in the excited larger vibration of cylinder element 43 part, utilize the vibration of this facilitated weight 8 (vibrating body), thus the vibration that can improve further based on collision and friction reduces performance.
In addition, cylinder element 43 and weight 8 (vibrating body) are all configured to motor drive shaft 7 roughly coaxial, are difficult to thus produce unbalanced force (out-of-balance force) when the rotation of armature spindle 11.In addition, be formed as weight 8 (vibrating body) to insert the state with the bolt 9 of motor drive shaft 7 arranged coaxial in the mode of matched in clearance, can be more difficult to thus produce unbalanced force (imbalance) when the rotation of armature spindle 11.And then because weight 8 is the ring bodies of plate shape, its center of gravity is the axle center of weight 8, be therefore more difficult to produce unbalanced force (out-of-balance force).
And then, due to configure multiple weight 8 in axial adjacent mode, therefore by making weight 8 collide vertically each other, rubbing also to make vibrational energy dissipate.
In addition, cylinder element 43 and weight 8 are accommodated in the space between the motor-side end face 7a and end member 10 of motor drive shaft 7, the axial length of helical-lobe compressor entirety can be formed as roughly the same with existing equipment thus.
In addition, the vibration frequency (being intended to the vibration frequency to armature spindle 11 additional attenuation) making the eigentone of cylinder element 43 and armature spindle 11 carry out resonating is coincide.That is, preferably make the eigentone of cylinder element 43 consistent with the eigentone of armature spindle 11, but this is only an example, does not need necessarily to make the eigentone of cylinder element 43 consistent with the eigentone of armature spindle 11.If the vibration frequency (being intended to the vibration frequency to armature spindle 11 additional attenuation) making the eigentone of cylinder element 43 and armature spindle 11 carry out resonating is coincide, then when producing resonance at armature spindle 11 (when being intended to the vibration of the vibration frequency of additional attenuation in armature spindle 11 generation), in the excited larger vibration of cylinder element 43 part, utilize the vibration of this facilitated weight 8, thus the vibration improved based on collision and friction reduces performance.
The vibration frequency that armature spindle 11 carries out resonating refers to, becomes large vibration frequency, comprise the eigentone of armature spindle 11 in the flexural vibrations of specific vibration mode lower rotor part axle 11.Further, being intended to the vibration frequency of armature spindle 11 additional attenuation is become large vibration frequency to the flexural vibrations of the armature spindle 11 that the running of helical-lobe compressor 1 counteracts, and comprises the eigentone of armature spindle 11.
In addition, in described helical-lobe compressor 1, one end of bolt 9 is fixed on the motor-side end face 7a of motor drive shaft 7 by screw-in etc., and the other end of bolt 9 (head 17) is abutted strongly with end member 10, thus to make bolt 9 by double base, but also only can be fixed in the end of motor-side end face 7a to bolt 9, or only be fixed in the end (head 17) of end member 10 pairs of bolts 9, make bolt 9 by cantilever support thus.
(the second embodiment)
Fig. 3 is the side generalized section of the helical-lobe compressor 102 illustrated involved by the second embodiment of the present invention.Fig. 4 is B portion enlarged drawing (Fig. 4 (a)) and the Y-Y sectional view (Fig. 4 (b)) thereof of Fig. 3.In Fig. 3 and Fig. 4, the component identical to the helical-lobe compressor 1 with the first embodiment marks identical Reference numeral.
Main difference point between the helical-lobe compressor 1 of the first embodiment and the helical-lobe compressor 102 of present embodiment is, in the helical-lobe compressor 102 of present embodiment, as vibrating body, uses multiple orbicule 44.
(orbicule)
Space between cylinder element 43 and bolt 9 is inserted in the mode of matched in clearance and is configured with multiple orbicule 44.The radial arrangement of orbicule 44 in the side of bolt 9 along armature spindle 11 has one.So, multiple orbicule 44 is layeredly be configured with one deck along the axis of armature spindle 11 in the side of bolt 9.In addition, multiple orbicule 44 is layeredly be configured with four layers around bolt 9.But, do not need must be four layers.
Identically with the weight 8 of the first embodiment, the axially-displaceable momentum of orbicule 44 is such as about 0.5mm ~ number mm, and the movable amount of axle orthogonal direction is such as about 0.02mm ~ about 0.5mm.In such a state, multiple orbicule 44 is arranging less gap each other, as a whole, is configured to motor drive shaft 7 roughly coaxial.
In addition, identically with the first embodiment, the eigentone of cylinder element 43 is such as consistent with the eigentone of armature spindle 11.
(effect, effect)
Identically with the helical-lobe compressor 1 of the first embodiment, according to helical-lobe compressor 102, for the flexural vibrations of the armature spindle 11 that the rotation of mainly screw rotor 41 causes, orbicule 44 (vibrating body) is impinging one another, friction, cylinder element 43, the axially end of travel (the motor-side end face 7a of motor drive shaft 7 and the end face of end member 10) etc. of front and back collide with orbicule 44 (vibrating body), rub, vibrational energy dissipates thus, and the vibration of armature spindle 11 reduces.That is, orbicule 44 can be utilized directly to reduce the vibration of the armature spindle 11 self rotated.
In addition, if make the eigentone of cylinder element 43 consistent with the eigentone of armature spindle 11, then near the eigentone of armature spindle 11, in the excited larger vibration of cylinder element 43 part, utilize this vibration to promote the vibration of orbicule 44 (vibrating body), thus the vibration that can improve further based on collision and friction reduce performance.
In addition, cylinder element 43 and orbicule 44 (orbicule 44 as a whole) are all configured to motor drive shaft 7 roughly coaxial, are difficult to thus produce unbalanced force (out-of-balance force) when the rotation of armature spindle 11.
In addition, in the present embodiment, be layeredly be configured to one deck along the axis of armature spindle 11 in the side of bolt 9 by multiple orbicule 44.Although also can space between cylinder element 43 and bolt 9, configure the orbicule 44 of more than two (double) along the radially adjoining of armature spindle 11 in the side of bolt 9, but be preferably as in the present embodiment, be layeredly configured to one deck along the axis of armature spindle 11 by multiple orbicule 44.Thus, be more difficult to produce unbalanced force (out-of-balance force) when the rotation of armature spindle 11.
If use the ball (steel ball etc.) of batch production product and market sale as orbicule 44 (vibrating body), then cost can be suppressed.
(variation)
In the present embodiment, although be configured with a cylinder element 43, one deck orbicule 44 (side of bolt 9) between revolving part 5 and bolt 9, but the orbicule 44 that stratiform also can be made to configure is stacked along the radially alternating of bolt 9 with cylinder element 43, become the stepped construction that the orbicule 44 that configured by stratiform is formed with cylinder element 43.
Fig. 5 is the Partial enlarged side generalized section of the variation that the helical-lobe compressor 1 shown in Fig. 1 and Fig. 2 is shown, arbitrary accompanying drawing is all the figure of the Fig. 2 (a) being equivalent to the part that helical-lobe compressor 1 is shown.
In the variation shown in Fig. 5 (a), the space between end member 10 and motor-side end face 7a not only configures cylinder element 43 and weight 8, also encloses viscoid 24.Utilize the inclosure of viscoid 24, viscous-damping can also be produced at the sliding surface of weight 8, consequently, utilize this viscous-damping also can reduce the vibration of armature spindle 11.At this, the sliding surface of weight 8 refers to, the face etc. that the face that weight 8 connects with by sliding axle portion 16, weight 8 connect with cylinder element 43.In addition, as viscoid 24, the high lubricating grease of viscosity, silicone oil etc. can be enumerated.The viscoid 24 of the viscosity of preferred about 10000cSt ~ 100000cSt., can space end member 10 and motor-side end face 7a between not only configure cylinder element 43 and orbicule 44, also enclose viscoid 24 in addition, in the helical-lobe compressor 102 of the second embodiment also in the same manner.
In addition, as shown in Fig. 5 (b), also the discoideus weight 27 of multiple atresia can be inserted along the inner face of cylinder element 43 space be configured between end member 10 (atresia) and motor-side end face 7a in the mode of matched in clearance.That is, the bolt 9 shown in Fig. 2 (a) can also be omitted.According to the manner too, the end of travel (the motor-side end face 7a of motor drive shaft 7 and the end face of end member 10) of cylinder element 43, axially front and back collides with weight 27 (vibrating body), rubs, vibrational energy dissipates thus, and the vibration of armature spindle 11 reduces.Further, discoideus weight 27 is configured to motor drive shaft 7 roughly coaxial, can be difficult to thus produce unbalanced force (out-of-balance force) when the rotation of armature spindle 11.And, coincide with the vibration frequency (such as the eigentone of armature spindle 11) be intended to armature spindle 11 additional attenuation by making the eigentone of cylinder element 43, thus when generation is intended to the vibration of the vibration frequency of additional attenuation, in the excited larger vibration of cylinder element 43 part, utilize this vibration to promote the vibration of weight 27, thus the vibration improved further based on collision and friction reduce performance.
Above, although be illustrated embodiments of the present invention, the present invention is not limited to above-mentioned embodiment, as long as the content described in the scope of Patent request, can carry out various change and be implemented.
Claims (4)
1. a helical-lobe compressor, is characterized in that,
Described helical-lobe compressor possesses:
Screw rotor;
Accommodate the screw rod shell of described screw rotor;
Motor drive shaft, this motor drive shaft and described screw rotor form as one structure, and in screw rotor side by cantilever support; And
Make the motor that described motor drive shaft rotates,
Described motor has:
Be fixed on the revolving part of the periphery of described motor drive shaft;
Be configured at the fixture in the outside of described revolving part; And
Accommodate the motor case of described revolving part and described fixture,
The motor-side end face of described motor drive shaft is positioned at the position leaning on screw rotor side than the motor-side end face of described revolving part,
Be fixed with end member at the motor-side end face of described revolving part, described end member is coaxial with described motor drive shaft,
Described helical-lobe compressor also possesses:
With described motor drive shaft roughly coaxial and along described revolving part inner face and insert the cylinder element in the space be configured between the motor-side end face of described motor drive shaft and described end member in the mode of matched in clearance; And
It is roughly coaxial and insert the vibrating body of the inner side being configured at described cylinder element in the mode of matched in clearance with described motor drive shaft,
The eigentone of described cylinder element is coincide with the vibration frequency that the armature spindle be made up of described screw rotor and described motor drive shaft carries out resonating.
2. helical-lobe compressor according to claim 1, is characterized in that,
The eigentone of described cylinder element is consistent with the eigentone of described armature spindle.
3. helical-lobe compressor according to claim 1 and 2, is characterized in that,
Described helical-lobe compressor also possesses bar-shaped by sliding component, this bar-shaped inner side being configured at described revolving part by sliding component, and coaxially arranges with described motor drive shaft, and the diameter of axle is less than the diameter of axle of described motor drive shaft,
Described vibrating body is the ring bodies of plate shape, and described vibrating body is inserted in described bar-shaped by sliding component in the mode of matched in clearance.
4. helical-lobe compressor according to claim 1 and 2, is characterized in that,
Described helical-lobe compressor also possesses bar-shaped by sliding component, this bar-shaped inner side being configured at described revolving part by sliding component, and coaxially arranges with described motor drive shaft, and the diameter of axle is less than the diameter of axle of described motor drive shaft,
Described vibrating body is inserted in described cylinder element and described bar-shaped by the multiple orbicules between sliding component in the mode of matched in clearance.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011-220645 | 2011-10-05 | ||
| JP2011220645A JP5500558B2 (en) | 2011-10-05 | 2011-10-05 | Screw compressor |
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| Publication Number | Publication Date |
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| CN103032325A CN103032325A (en) | 2013-04-10 |
| CN103032325B true CN103032325B (en) | 2015-04-29 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201210356941.XA Active CN103032325B (en) | 2011-10-05 | 2012-09-21 | Screw compressor |
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| Country | Link |
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| JP (1) | JP5500558B2 (en) |
| KR (1) | KR101376023B1 (en) |
| CN (1) | CN103032325B (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN104235031A (en) * | 2013-06-19 | 2014-12-24 | 重庆美的通用制冷设备有限公司 | Multistage cantilever compressor |
| JP6324233B2 (en) * | 2014-06-25 | 2018-05-16 | Ｂｉｇ Ｄａｉｓｈｏｗａ株式会社 | Anti-vibration structure of rotating body |
| CN104454524A (en) * | 2014-11-18 | 2015-03-25 | 杭州久益机械有限公司 | Female-male screw rod rotor synchronous frequency-conversion integrated compressor machine head |
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| SU526712A2 (en) * | 1975-03-04 | 1976-08-30 | Предприятие П/Я В-8673 | Screw machine |
| US4557679A (en) * | 1983-11-30 | 1985-12-10 | Hitachi, Ltd. | Rotary fluid machine with thrust bearing mounting unit |
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| CN102168675A (en) * | 2010-02-26 | 2011-08-31 | 株式会社神户制钢所 | Spial compressor |
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| JPS55148995A (en) * | 1979-05-11 | 1980-11-19 | Hitachi Ltd | Screw compressor |
| JPS6134366A (en) * | 1984-07-26 | 1986-02-18 | Matsushita Electric Ind Co Ltd | Vibration reducing device for compressor |
| JPH0533787A (en) * | 1991-07-31 | 1993-02-09 | Kobe Steel Ltd | Screw compressor |
| JP2993807B2 (en) * | 1992-10-23 | 1999-12-27 | トリニティ工業株式会社 | Exhaust treatment device for painting booth with air supply |
| JP2002191154A (en) | 2000-12-19 | 2002-07-05 | Nippon Otis Elevator Co | Motor |
| JP4190803B2 (en) * | 2002-05-23 | 2008-12-03 | 株式会社神戸製鋼所 | Vibration control device |
| JP5045456B2 (en) * | 2007-08-01 | 2012-10-10 | 日本精工株式会社 | Spindle device |
| JP5265987B2 (en) | 2008-08-11 | 2013-08-14 | オークマ株式会社 | Vibration control device for machine tools |
| JP5197487B2 (en) | 2009-05-22 | 2013-05-15 | 株式会社神戸製鋼所 | Screw compressor |
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2012
- 2012-09-21 CN CN201210356941.XA patent/CN103032325B/en active Active
- 2012-10-04 KR KR1020120109954A patent/KR101376023B1/en active IP Right Grant
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| SU526712A2 (en) * | 1975-03-04 | 1976-08-30 | Предприятие П/Я В-8673 | Screw machine |
| US4557679A (en) * | 1983-11-30 | 1985-12-10 | Hitachi, Ltd. | Rotary fluid machine with thrust bearing mounting unit |
| CN2625602Y (en) * | 2003-04-30 | 2004-07-14 | 良峰塑胶机械股份有限公司 | Multi-stag vacuum pump |
| CN101334027A (en) * | 2007-06-29 | 2008-12-31 | 上海汉钟精机股份有限公司 | Frequency conversion screw type cold compressor three-support structure |
| CN102168675A (en) * | 2010-02-26 | 2011-08-31 | 株式会社神户制钢所 | Spial compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| KR20130037177A (en) | 2013-04-15 |
| CN103032325A (en) | 2013-04-10 |
| JP5500558B2 (en) | 2014-05-21 |
| JP2013079620A (en) | 2013-05-02 |
| KR101376023B1 (en) | 2014-03-19 |
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Effective date of registration: 20220225 Address after: Tokyo, Japan Patentee after: Shengang Compressor Co.,Ltd. Address before: Japan Hyogo Prefecture Patentee before: Kobe Steel, Ltd. |
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