CN103032325A - Screw compressor - Google Patents
Screw compressor Download PDFInfo
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- CN103032325A CN103032325A CN201210356941XA CN201210356941A CN103032325A CN 103032325 A CN103032325 A CN 103032325A CN 201210356941X A CN201210356941X A CN 201210356941XA CN 201210356941 A CN201210356941 A CN 201210356941A CN 103032325 A CN103032325 A CN 103032325A
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- Prior art keywords
- drive shaft
- motor drive
- motor
- helical
- rotor
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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
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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
- 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
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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
- Y10S417/00—Pumps
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 type.
Background technique
The helical-lobe compressor ratio of the direct connecting arrangement of motor is high via the device effciency of energy transfer of the power delivery mode of rotating band.And, having used in the helical-lobe compressor of rotating speed control mode of transducer in employing, the helical-lobe compressor of the direct connecting arrangement of motor becomes main flow.At this, from reducing the purpose of cost, minimizing mechanical loss, mostly form one-sided directly binding type of the motor 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 so that cal speed adopts the design of rotor-shaft system considerably beyond the mode of running rotating speed.Yet in the helical-lobe compressor of the excitation force that produces the pressure pulsation composition, well below the rotation speed operation of the cal speed (rotating speed) of rotor shaft the time, the vibration of rotor-shaft system part becomes large sometimes.And, high order composition in the vibration that the imbalance that is determined by the axle rotating speed causes is waiting because of rocking of rotor-shaft system in the situation of significantly appearance, sometimes still when being lower than the rotation speed operation of cal speed (rotating speed), the vibration of rotor-shaft system part becomes large.
At this, as the method for the vibration that reduces helical-lobe compressor, method based on the such arrangement for damping oscillations of the dynamic vibration absorber that uses vibration-proof rubber arranged, become the method that the mode of large rotary speed area is controlled the rotating speed of rotor shaft to skip vibration.
Yet, in the method for the arrangement for damping oscillations such based on dynamic vibration absorber, there is following problem: when changing because of the condition that arranges that causes vibration-proof rubber part etc. such as lax deteriorated, that install of rubber, the resonant frequency of rotor-shaft system part changes, and can not obtain vibration-damping effect.And in the situation of the helical-lobe compressor of rotating speed control mode that adopt to use transducer, only having the dynamic vibration absorber of attenuating in characteristic frequency can not be corresponding with the vibration of whole rotary speed area.
On the other hand, in the method for the rotating speed of rotor shaft being controlled in the mode of skipping the large rotary speed area of vibration change, in the situation of safety, also need to skip the rotary speed area of the large rotating speed periphery of vibration change, sometimes the real machine operating condition is counteracted.
As irrelevant and can reduce the method (can reduce the method for the vibration of whole rotary speed area) of vibration with the eigentone of helical-lobe compressor, has the method that patent documentation 1 is for example put down in writing.Record a kind of helical-lobe compressor in patent documentation 1, this helical-lobe compressor is characterised in that, being arranged at motor case with the clava along continuous straight runs is outstanding, and the plate (mass body) that will have a hole inserts this clava, and this hole has larger play.According to this structure, because the vibration of motor case causes plate (mass body) to carry out displacement at above-below direction, the outstanding clava that is arranged at motor case bumps with plate (mass body) and consumes vibrational energy, thus the vibration of minimizing motor case.
Technical paper formerly
Patent documentation
Patent documentation 1: TOHKEMY 2003-343641 communique
At this, in the situation of directly binding type of the motor helical-lobe compressor of cantilevered fashion, when the rotor-shaft system vibration partly of this helical-lobe compressor became large, the whirling vibration of rotor shaft significantly became large, and the revolving part of motor and the distance between the fixed block broaden or narrow down.At this moment, because the magnetic attraction that acts between revolving part and the fixed block changes, therefore be not only revolving part and be subject to impact based on magnetic attraction, the fixed block side also is subject to the impact based on magnetic attraction, and the motor case that is provided with fixed block is subject to magnetic attraction and is vibrated by exciting.Like this, be not only the revolving part side of motor and vibrate, the fixed block side is also vibrated, and the revolving part of motor and motor case vibrate under the state of coupling thus, along with this vibration aggravation revolving part is contacted with fixed block.Consequently, sometimes fixed block side damage and produce the state that is difficult to continuous running.
As mentioned above, in the vibration methods to reduce noises that patent documentation 1 is put down in writing, utilize to give prominence to be arranged at the clava of motor case and to insert the vibration that this claval plate (mass body) that can carry out along the vertical direction displacement reduces " motor case ".Therefore, can not cause because of the effect of the vibration of motor case the vibration of revolving part side to increase.Yet, in the situation of large in the vibration of the rotor shaft self of helical-lobe compressor, as to form the permission load that for example surpasses bearing vibration, need to take some vibration countermeasures to the rotor shaft self of helical-lobe compressor.In addition, rotor shaft self is being taked to vibrate in the situation of countermeasure, the mode that this vibration countermeasure must the unbalanced force (unbalanced force) when avoiding the rotation as rotor shaft acts on is discussed.
In addition, be arranged at the clava of motor case and insert in the such structure of this claval plate (mass body) that can carry out along the vertical direction displacement outstanding, need to guarantee to dispose the space of clava and plate (mass body) in the outside of motor case, sometimes become the restriction of the assembling layout of compressor.And, also become be used to obtaining thermally equilibrated restriction.
Summary of the invention
The present invention finishes in view of above-mentioned actual conditions, its purpose is to provide a kind of directly binding type of motor helical-lobe compressor that possesses the cantilevered fashion of vibration damping structure, this vibration damping structure is difficult to produce unbalanced force (unbalanced force) when the rotation of rotor shaft, and can directly reduce the vibration of rotor shaft 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 the described screw rotor structure that forms as one, and in the screw rotor side by cantilever support; And the motor that makes described motor drive shaft rotation, described motor has: the revolving part that is fixed in the periphery of described motor drive shaft; Be disposed at the fixed block in the outside of described revolving part; And the motor case of accommodating described revolving part and described fixed block, the motor-side end face of described motor drive shaft is positioned at the position of leaning on the screw rotor side than the motor-side end face of described revolving part, motor-side end face at described revolving part is fixed with end member, this end member is coaxial with described motor drive shaft, and described helical-lobe compressor also possesses: roughly coaxial and along the inner face of described revolving part and insert the motor-side end face that is disposed at described motor drive shaft and the cylinder element in the space between the described end member in the mode of Spielpassung with described motor drive shaft; And roughly coaxial and insert the oscillating body of the inboard that is disposed at described cylinder element in the mode of Spielpassung with described motor drive shaft, the eigentone of described cylinder element is coincide with the vibration frequency that the rotor shaft that is made of described screw rotor and described motor drive shaft resonates.
According to this structure, for the flexure vibrations of rotor shaft, the end of travel (for example, the motor-side end face of motor drive shaft) by cylinder element, before and after axially etc. and oscillating body collision, friction, vibrational energy dissipates thus, and the vibration of rotor shaft reduces.And, the vibration frequency that eigentone by making cylinder element and rotor shaft resonate is coincide, thus when when rotor shaft produces resonance, partly encouraged larger vibration at cylinder element, utilize the vibration of this facilitated oscillating body, reduce performance thereby further improve based on collision and the vibration that rubs.
In addition, cylinder element and oscillating body are configured to motor drive shaft roughly coaxial, are difficult to thus produce when the rotation of rotor shaft unbalanced force (unbalanced force).
The invention effect
According to the present invention, be difficult to when the rotation of rotor shaft, produce unbalanced force (unbalanced force), and can directly reduce the vibration of rotor shaft self.
Description of drawings
Fig. 1 is the side generalized section that the related helical-lobe compressor of the first mode of execution of the present invention is shown.
Fig. 2 is A section enlarged view and the X-X sectional view thereof of Fig. 1.
Fig. 3 is the side generalized section that the related helical-lobe compressor of the second mode of execution of the present invention is shown.
Fig. 4 is B section enlarged view and the Y-Y sectional view thereof of Fig. 3.
Fig. 5 is the local Zoom Side generalized section that the variation of Fig. 1 and helical-lobe compressor shown in Figure 2 is shown.
The explanation of reference character
1: helical-lobe compressor
2: the screw rod main part
3: screw axis
5: revolving part
6: fixed block
7: motor drive shaft
8: weight (oscillating body)
9: bolt (bar-shaped by slide member)
10: end member
11: rotor shaft
12: the screw rod shell
13: motor case
30: motor part (motor)
41: screw rotor
43: cylinder element
Embodiment
Below, describe being used for implementing mode of the present invention with reference to accompanying drawing.
(the first mode of execution)
Fig. 1 is the side generalized section that the related helical-lobe compressor 1 of the first mode of execution of the present invention is shown.Fig. 2 is A section enlarged view (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 that possesses the direct connecting arrangement of motor that screw rod main part 2 and motor part 30 (motor) form.
(screw rod main part)
The screw rod shell 12 that screw rod main part 2 has screw rotor 41 and accommodates screw rotor 41.Screw rotor 41 have screw rod tooth section 4 and with screw rod tooth section 4 coaxial and with the form as one screw axis 3 of structure of this screw rod tooth section 4.Screw axis 3 is by bearing 14 and bearing 15 dual-supportings.
Screw rod tooth section 4 and screw axis 3 by steel by cutting etc. and manufactured.In addition, also can after making separately respectively screw rod tooth section 4 and screw axis 3, carry out rigid joint (one binding).And, screw rotor 41 and motor drive shaft 7 described later also by steel by the manufacturings such as the cutting structure that forms as one.Consisted of the rotor shaft 11 of rotation by the screw rotor 41 of the structure that mutually forms as one and motor drive shaft 7.In addition, also can after making separately respectively screw rotor 41 and motor drive shaft 7, carry out rigid joint (one binding).As the method for rigid joint (integrative-structure), has flange binding etc.
(motor part)
Motor part 30 (motor) is be used to the driving source that makes rotor shaft 11 rotations, has: the revolving part 5 that is fixed in the periphery of motor drive shaft 7; Be disposed at the fixed block 6 in the outside of revolving part 5; And the motor case 13 of accommodating revolving part 5 and fixed block 6.Motor drive shaft 7 with screw rotor 41 (screw axis 3) coaxial and with screw rotor 41 (screw axis 3) structure that forms as one, and in screw rotor 41 sides by cantilever support.Specifically, motor drive shaft 7 is by the bearing 14 of screw rotor 41 sides (and bearing 15) cantilever support.
The motor-side end face 7a of motor drive shaft 7 is positioned at the position of leaning on screw rotor 41 sides than the motor-side end face 5a of revolving part 5.Utilize bolt (not shown) etc. to be fixed with discoideus end member 10 at the motor-side end face 5a of revolving part 5.Offer porose 10a at the center of end member 10.End member 10 is made as with motor drive shaft 7 coaxial.
(damper mechanism section)
Be inserted with cylinder element 43 at the motor-side end face 7a of motor drive shaft 7 and the space between the end member 10.Cylinder element 43 and motor drive shaft 7 are roughly coaxial and insert along the inner face of revolving part 5 and in the mode of Spielpassung and to be disposed at revolving part 5, end member 10 and motor drive shaft 7.
Length Ratio motor-side end face 7a and the interval between the end member 10 of cylinder element 43 are little.The axially-displaceable momentum of cylinder element 43 is for example about 0.5mm～number mm.And 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 the fixed block 6, for example, 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 (at the rotating center of motor drive shaft 7) be fixed with bolt 9.The bolt 9 that is disposed at the inboard of revolving part 5 is involved in the present invention bar-shaped by an example of slide member.
Shown in Fig. 2 (a), bolt 9 comprises: be fixed in the state that connects the hole 10a in end member 10, be formed centrally motor drive shaft 7 motor-side end face 7a by slip axial region 16 and be formed at by the head 17 (large-diameter portion) of the end of slip axial region 16.The external diameter of head 17 is than large by the diameter of axle of slip axial region 16.Less than the diameter of axle of motor drive shaft 7 by the diameter of axle of slip axial region 16.
At this, contain in the inboard of cylinder element 43 a plurality of tabular and be the weight 8 of ring-type, this weight 8 form mode with Spielpassung be inserted in bolt 9 by the state of slip axial region 16.In the present embodiment, although form six weights 8, be not limited to six.Also can be one.Weight 8 is examples of the ring bodies (oscillating body) of the plate shape among the present invention.
Thickness Ratio motor-side end face 7a and the interval between the end member 10 of the total of six weights 8 are little.That is, weight 8 can moving axially along motor drive shaft 7.The axially-displaceable momentum of weight 8 is for example about 0.5mm～number mm.And the external diameter of weight 8 (diameter) is less than the internal diameter of cylinder element 43.And, as mentioned above and since weight 8 with the mode of Spielpassung be inserted in bolt 9 by slip axial region 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 the fixed block 6, is for example about 0.02mm～about 0.5mm.
At this, in Fig. 2 (a), weight 8 is illustrated as with motor drive shaft 7 coaxial.Yet, make under weight 8 state static with being by slip axial region 16 of the mode inserting bolt 9 of Spielpassung, strictly speaking, the axle center that forms weight 8 reduces the state of the movable amount of axle orthogonal direction (about 0.02mm～0.5mm) of weight 8 than the axle center of motor drive shaft 7 direction under the vertical.That is, in the present invention, weight 8 (oscillating body) be configured to the coaxial expression of motor drive shaft 7 " roughly " be that the axle center that forms weight 8 (oscillating body) reduces the state of the movable amount of this axle orthogonal direction than the axle center of motor drive shaft 7 direction under the vertical.
Also be in the same manner about cylinder element 43, in the present invention, cylinder element 43 be configured to the coaxial expression of motor drive shaft 7 " roughly " be that the axle center that forms cylinder element 43 reduces the state of the movable amount of this axle orthogonal direction (about 0.02mm～0.5mm) than the axle center of motor drive shaft 7 direction under the vertical.
So, weight 8 is to become roughly coaxial with motor drive shaft 7 with member around the motor-side end face 7a of motor drive shaft 7, the end member 10 etc. in the state configuration that bumps such as axial.In the present embodiment, owing to use a plurality of weights 8, therefore a plurality of weights 8 also form in axially mutually collision.
In addition, although be circular by the sectional shape of slip axial region 16, it must be circular not needing, and for example, also can be quadrilateral etc.The hole 8a that is formed at the center of weight 8 also is identical, also can not be circular but such as quadrilateral etc.Be formed at weight 8 the center hole 8a shape with coincide by the sectional shape of slip axial region 16.And although the 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, make the eigentone of cylinder element 43 consistent with the eigentone of the rotor shaft 11 that is consisted of by screw rotor 41 and motor drive shaft 7.The eigentone of rotor shaft 11 is for example considered with the parts of rotor shaft 11 one rotation, is the parts of rotor shaft 11, revolving part 5, bolt 9 and end member 10 and so on and obtains by calculating.The eigentone of cylinder element 43 is by selecting its length, thickness, external diameter, internal diameter and material etc. to be adjusted.
(effect, effect)
According to helical-lobe compressor 1, the flexure vibrations of the rotor shaft 11 that causes for the rotation that mainly is screw rotor 41, 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, axial front and back and weight 8 (oscillating body) collision, friction, vibrational energy dissipates (based on the dissipation of the vibrational energy of axial impact) thus, and the vibration of rotor shaft 11 reduces.That is the vibration of the rotor shaft 11 that, can utilize the weight 8 that bumps axially waiting movement directly to reduce to rotate self.And, owing to become near an opposite side end (end member 10) the configuration weight 8 that large part is the cantilever support side of motor drive shaft 7 in the flexure vibrations of rotor shaft 11, can further improve thus the dissipation efficiency based on the vibrational energy of axial impact.
In addition, make the eigentone of cylinder element 43 consistent with the eigentone of rotor shaft 11, thus near the eigentone of rotor shaft 11, encouraged larger vibration in cylinder element 43 parts, utilize the vibration of this facilitated weight 8 (oscillating body), thereby can further improve based on the vibration minimizing performance of collision with friction.
In addition, cylinder element 43 and weight 8 (oscillating body) all are configured to motor drive shaft 7 roughly coaxial, are difficult to thus produce when the rotation of rotor shaft 11 unbalanced force (unbalanced force).In addition, form weight 8 (oscillating body) is inserted state with the bolt 9 of motor drive shaft 7 arranged coaxial in the mode of Spielpassung, can more be difficult to thus when the rotation of rotor shaft 11, produce unbalanced force (imbalance).And then because weight 8 is the ring bodies of plate shape, its center of gravity is the axle center of weight 8, therefore more is difficult to produce unbalanced force (unbalanced force).
And then, owing to dispose a plurality of weights 8 in axial adjacent mode, therefore by making weight 8 collide vertically each other, rub vibrational energy is dissipated.
In addition, accommodate cylinder element 43 and weight 8 in motor-side end face 7a and the space between the end member 10 of motor drive shaft 7, the axial length of helical-lobe compressor integral body can be formed with existing equipment thus roughly the same.
In addition, the eigentone of cylinder element 43 and vibration frequency (being intended to the vibration frequency of rotor shaft 11 additional attenuations) that rotor shaft 11 resonates being coincide gets final product.That is, preferably make the eigentone of cylinder element 43 consistent with the eigentone of rotor shaft 11, but this only is an example, does not need necessarily to make the eigentone of cylinder element 43 consistent with the eigentone of rotor shaft 11.If making the eigentone of cylinder element 43 and vibration frequency (being intended to the vibration frequency of rotor shaft 11 additional attenuations) that rotor shaft 11 resonates coincide, then when when rotor shaft 11 produces resonance (when when rotor shaft 11 produces the vibration of the vibration frequency that is intended to additional attenuation), encouraged larger vibration in cylinder element 43 parts, utilize the vibration of this facilitated weight 8, thereby improve based on the vibration minimizing performance of collision with friction.
The vibration frequency that rotor shaft 11 resonates refers to, in the large vibration frequency of flexure vibrations change of specific vibrational mode lower rotor part axle 11, comprises the eigentone of rotor shaft 11.And being intended to the vibration frequency of rotor shaft 11 additional attenuations is that the flexure vibrations of the rotor shaft 11 that counteracts of the running to helical-lobe compressor 1 become large vibration frequency, comprises the eigentone of rotor shaft 11.
In addition, in described helical-lobe compressor 1, one end of bolt 9 is waited the motor-side end face 7a that is fixed in motor drive shaft 7 by screwing in, and the other end (head 17) that makes bolt 9 and end member 10 be butt strongly, thus so that bolt 9 by dual-supporting, but also can only be fixed the end of bolt 9 at motor-side end face 7a, perhaps only be fixed in the end of 10 pairs of bolts 9 of end member (head 17), thus so that bolt 9 by cantilever support.
(the second mode of execution)
Fig. 3 is the side generalized section that the related helical-lobe compressor 102 of the second mode of execution of the present invention is shown.Fig. 4 is B section enlarged view (Fig. 4 (a)) and the Y-Y sectional view (Fig. 4 (b)) thereof of Fig. 3.In Fig. 3 and Fig. 4, the reference character identical to the member mark identical with the helical-lobe compressor 1 of the first mode of execution.
Main difference point between the helical-lobe compressor 1 of the first mode of execution and the helical-lobe compressor 102 of present embodiment is in the helical-lobe compressor 102 of present embodiment, as oscillating body, to use a plurality of spheroids 44.
(spheroid)
Space between cylinder element 43 and bolt 9 is inserted in the mode of Spielpassung and is disposed a plurality of spheroids 44.Spheroid 44 has one in a side of bolt 9 along the radial arrangement of rotor shaft 11.So, a plurality of spheroids 44 layeredly dispose one deck in a side of bolt 9 along axially being of rotor shaft 11.In addition, a plurality of spheroids 44 are around bolt 9 and layeredly dispose four layers.But not needing must be four layers.
With the weight 8 of the first mode of execution in the same manner, the axially-displaceable momentum of spheroid 44 is for example about 0.02mm～about 0.5mm for for example about 0.5mm～number mm, the movable amount of axle orthogonal direction.Under such state, a plurality of spheroids 44 as a whole, are configured to motor drive shaft 7 roughly coaxial in that less gap is set each other.
In addition, with the first mode of execution in the same manner, the eigentone of the cylinder element 43 for example eigentone with rotor shaft 11 is consistent.
(effect, effect)
With the helical-lobe compressor 1 of the first mode of execution in the same manner, according to helical-lobe compressor 102, the flexure vibrations of the rotor shaft 11 that causes for the rotation that mainly is screw rotor 41, spheroid 44 (oscillating body) collides each other, rubs, 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, axial front and back etc. and spheroid 44 (oscillating body) collision, friction, vibrational energy dissipates thus, and the vibration of rotor shaft 11 reduces.That is, can utilize spheroid 44 directly to reduce the vibration of the rotor shaft 11 self of rotation.
In addition, if make the eigentone of cylinder element 43 consistent with the eigentone of rotor shaft 11, then near the eigentone of rotor shaft 11, encouraged larger vibration in cylinder element 43 parts, utilize this vibration of vibrating to promote spheroid 44 (oscillating body), thereby can further improve based on the vibration minimizing performance of collision with friction.
In addition, cylinder element 43 and spheroid 44 (spheroid 44 as a whole) all are configured to motor drive shaft 7 roughly coaxial, are difficult to thus produce when the rotation of rotor shaft 11 unbalanced force (unbalanced force).
In addition, in the present embodiment, a plurality of spheroids 44 layeredly are configured to one deck in a side of bolt 9 along axially being of rotor shaft 11.Although space that also can be between cylinder element 43 and bolt 9, in a side of bolt 9 along the spheroid 44 more than the radially adjoining configuration of rotor shaft 11 two (double), but preferred as present embodiment, a plurality of spheroids 44 are along the axial of rotor shaft 11 layeredly are configured to one deck.Thus, more be difficult to when the rotation of rotor shaft 11, produce unbalanced force (unbalanced force).
If the ball (steel ball etc.) that use batch production product are market to be sold then can suppress cost as spheroid 44 (oscillating body).
(variation)
In the present embodiment, although between revolving part 5 and bolt 9, dispose a cylinder element 43, one deck spheroid 44 (side of bolt 9), but also can make the spheroid 44 of stratiform configuration stacked along the radially alternating of bolt 9 with cylinder element 43, become the stepped construction that is consisted of by the spheroid 44 of stratiform configuration and cylinder element 43.
Fig. 5 is the local Zoom Side generalized section that the variation of Fig. 1 and helical-lobe compressor 1 shown in Figure 2 is shown, and arbitrary accompanying drawing all is the figure of Fig. 2 (a) that is equivalent to illustrate the part of helical-lobe compressor 1.
In the variation shown in Fig. 5 (a), the space between end member 10 and motor-side end face 7a not only disposes cylinder element 43 and weight 8, also encloses viscous body 24.Utilize the inclosure of viscous body 24, can also produce viscous damping at the slip surface of weight 8, consequently, utilize this viscous damping also can reduce the vibration of rotor shaft 11.At this, the slip surface of weight 8 refers to, the face that weight 8 and the face that is joined by slip axial region 16, weight 8 and cylinder element 43 join etc.In addition, as viscous body 24, can enumerate the high lubricating grease of viscosity, silicone oil etc.The viscous body 24 of the viscosity about preferred 10000cSt～100000cSt.In addition, in the helical-lobe compressor 102 of the second mode of execution, also in the same manner, can not only dispose cylinder element 43 and spheroid 44 in the space between end member 10 and motor-side end face 7a, also enclose viscous body 24.
In addition, shown in Fig. 5 (b), also the discoideus weight 27 of a plurality of atresias can be inserted the space that is disposed between end member 10 (atresia) and the motor-side end face 7a along the inner face of cylinder element 43 and in the mode of Spielpassung.That is, also can omit the bolt 9 shown in Fig. 2 (a).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, axial front and back and weight 27 (oscillating body) collision, friction, vibrational energy dissipates thus, and the vibration of rotor shaft 11 reduces.And, discoideus weight 27 is configured to motor drive shaft 7 roughly coaxial, can be difficult to thus when the rotation of rotor shaft 11 to produce unbalanced force (unbalanced force).And, coincide by the eigentone that makes cylinder element 43 and the vibration frequency (for example eigentone of rotor shaft 11) that is intended to rotor shaft 11 additional attenuations, thus when producing the vibration of the vibration frequency that is intended to additional attenuation, encouraged larger vibration in cylinder element 43 parts, utilize this vibration of vibrating to promote weight 27, reduce performance thereby further improve based on collision and the vibration that rubs.
More than, although embodiments of the present invention are illustrated, the present invention is not limited to above-mentioned mode of execution, so long as the content that the scope of patent request is put down in writing can be carried out various changes and also 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 the described screw rotor structure that forms as one, and in the screw rotor side by cantilever support; And
Make the motor of described motor drive shaft rotation,
Described motor has:
Be fixed in the revolving part of the periphery of described motor drive shaft;
Be disposed at the fixed block in the outside of described revolving part; And
Accommodate the motor case of described revolving part and described fixed block,
The motor-side end face of described motor drive shaft is positioned at the position of leaning on the screw rotor side than the motor-side end face of described revolving part,
Motor-side end face at described revolving part is fixed with end member, and described end member is coaxial with described motor drive shaft,
Described helical-lobe compressor also possesses:
Roughly coaxial and along the inner face of described revolving part and insert the motor-side end face that is disposed at described motor drive shaft and the cylinder element in the space between the described end member in the mode of Spielpassung with described motor drive shaft; And
It is roughly coaxial and insert the oscillating body of the inboard that is disposed at described cylinder element in the mode of Spielpassung with described motor drive shaft,
The eigentone of described cylinder element is coincide with the vibration frequency that the rotor shaft that is made of described screw rotor and described motor drive shaft resonates.
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 rotor shaft.
3. helical-lobe compressor according to claim 1 and 2 is characterized in that,
Described helical-lobe compressor also possesses bar-shaped by slide member, and this is bar-shaped to be disposed at the inboard of described revolving part by slide member, and with the coaxial setting of described motor drive shaft, the diameter of axle is less than the diameter of axle of described motor drive shaft,
Described oscillating body is that the mode with Spielpassung is inserted in described bar-shaped by the ring bodies of the plate shape of slide member.
4. helical-lobe compressor according to claim 1 and 2 is characterized in that,
Described helical-lobe compressor also possesses bar-shaped by slide member, and this is bar-shaped to be disposed at the inboard of described revolving part by slide member, and with the coaxial setting of described motor drive shaft, the diameter of axle is less than the diameter of axle of described motor drive shaft,
Described oscillating body is that the mode with Spielpassung is inserted in described cylinder element and described bar-shaped by a plurality of spheroids between the slide member.
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 true CN103032325A (en) | 2013-04-10 |
| CN103032325B CN103032325B (en) | 2015-04-29 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210356941.XA Active CN103032325B (en) | 2011-10-05 | 2012-09-21 | Screw compressor |
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| Country | Link |
|---|---|
| JP (1) | JP5500558B2 (en) |
| KR (1) | KR101376023B1 (en) |
| CN (1) | CN103032325B (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| 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 |
| CN106457497A (en) * | 2014-06-25 | 2017-02-22 | 大昭和精机株式会社 | Vibration-proof structure for rotating body |
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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 |
| CN106457497A (en) * | 2014-06-25 | 2017-02-22 | 大昭和精机株式会社 | Vibration-proof structure for 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 |
Also Published As
| Publication number | Publication date |
|---|---|
| JP5500558B2 (en) | 2014-05-21 |
| JP2013079620A (en) | 2013-05-02 |
| KR20130037177A (en) | 2013-04-15 |
| CN103032325B (en) | 2015-04-29 |
| KR101376023B1 (en) | 2014-03-19 |
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