CN102168675B - Spial compressor - Google Patents
Spial compressor Download PDFInfo
- Publication number
- CN102168675B CN102168675B CN201110042120.4A CN201110042120A CN102168675B CN 102168675 B CN102168675 B CN 102168675B CN 201110042120 A CN201110042120 A CN 201110042120A CN 102168675 B CN102168675 B CN 102168675B
- Authority
- CN
- China
- Prior art keywords
- weight
- motor
- rotor
- screw compressor
- motor reel
- 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.)
- Active
Links
Images
Landscapes
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The invention provides a cantilever type motor coupled spiral compressor with a vibration damping structure. The vibration damping structure can directly reduce the self-vibration of a rotor shaft while not easily generating an unbalanced force at the time of the stator shaft rotation. The spiral compressor (1) comprises a spiral rotor (4), a spiral shaft (3) which is coaxial with a male rotor (4a) of the spiral rotor (4) and is an integrated structure with respect to the male rotor (4a), a motor shaft (7) which is coaxial with the spiral shaft (3) and is an integrated structure with respect to the spiral shaft (3) and is supported by a cantilever at the side of the spiral rotor, and a motor enabling the motor shaft (7) to rotate. The spiral compressor (1) also comprises a bolt (9) which is coaxial with the motor shaft (7) and is fixed to the motor side end face (7a) of the motor shaft (7) with a shaft diameter being smaller than that of the motor shaft (7), and a circular weight (8) which is loosely inserted in the bolt (9). The axial distance-to-go of the weight is larger than the displaceable amount in a direction orthogonal to the shaft.
Description
Technical field
The present invention relates to screw type compressor.
Background technique
The screw compressor utilization of motor direct coupled structure is via the power delivery mode of rotating band, and therefore energy conversion efficiency is high.In addition, used in the screw compressor of rotating speed control mode of transducer in employing, the screw compressor of motor direct coupled structure becomes main flow.Here from reducing costs, cut down the object of mechanical loss, be in most cases formed in the motor direct linkage type screw compressor of the one-sided cantilevered fashion that bearing is not set of motor reel.
During for the screw compressor of cantilevered fashion, conventionally rotor axial system is designed to cal speed far away higher than running rotating speed.But, producing in the screw compressor of encouraging the power of shaking of pressure pulsation composition, there is following situation: the vibration dividing at the rotating speed lower rotor part axle pastern of the cal speed well below rotor shaft (rotating speed) becomes large.In addition, in the case of the high order composition of the caused vibration of imbalance determined by axle rotating speed because of rocking of rotor axial system etc. export significantly such, also exist the vibration dividing at the rotating speed lower rotor part axle pastern lower than cal speed (rotating speed) to become large situation.
Here, as the method for vibration that reduces screw compressor, the known method that has the method for the such arrangement for damping oscillations of dynamic vibration absorber based on having used vibration-proof rubber or become the rotating speed of the mode control rotor shaft of large rotary speed area to skip vibration.
But, in the method for the arrangement for damping oscillations such based on dynamic vibration absorber, there are the following problems: if because the deteriorated of rubber or the condition that arranges that causes vibration-proof rubber part etc. such as lax of installing change, and the variation of resonant frequency of rotor axial system part and cannot obtain vibration-damping effect.In addition, in the case of having used the screw compressor of rotating speed control mode of transducer for adopting, the dynamic vibration absorber that only characteristic frequency is had to an attenuating cannot be tackled the vibration in whole rotary speed area.
On the other hand, in the method for the rotating speed to skip the mode control rotor shaft that vibrates the rotary speed area that becomes large, there is following situation: for the rotary speed area of the large rotating speed periphery of vibration change, also need to skip based on security consideration, thereby bring obstacle to physical device operating condition.
As the method (reducing the vibration in whole rotary speed area) that can independently reduce with the natural vibration number of screw compressor vibration, known have a method as described in Patent Document 1 of example.In patent documentation 1, record screw compressor as described below, it is characterized in that, clava has been arranged to substantially horizontal is outstanding with respect to motor case, the plate (mass body) having with the hole of larger play has been inserted into this clava.According to this structure, because the vibration of motor case causes plate (mass body) direction displacement up and down, outstanding clava and the plate (mass body) being arranged on motor case collides and consumes vibrational energy, thereby reduces the vibration of motor case.
[patent documentation 1] TOHKEMY 2003-343641 communique
Here, in the case of being the motor direct linkage type screw compressor of cantilevered fashion, if it is large that the vibration of the rotor axial system part of this screw compressor becomes, the vibration of the whirling of rotor shaft significantly becomes large, and the distance between rotor and the stator of motor broadens or narrows.Now, change owing to acting on magnetic attraction between rotor and stator, therefore not only rotor-side is subject to the impact of magnetic attraction, and stator side is also subject to the impact of magnetic attraction, and the motor case that is provided with stator is encouraged and shaken and vibrate by magnetic attraction.Like this, the not only rotor-side of motor vibration, stator side is also vibrated, and has thus following situation: the state vibration to be coupled such of the rotor of motor and motor case, contacts with stator along with this vibration increases rotor.Consequently, there is stator side damage and occur the state that is difficult to remain in operation.
As previously mentioned, in the vibration reduction method of recording at patent documentation 1, by the outstanding plate (mass body) that is arranged on the clava on motor case and is inserted into this claval displacement along the vertical direction, reduce the vibration of " motor case ".Therefore, can not increase because the effect of the vibration of motor case causes the vibration of rotor-side.But, in the case of the vibration of the rotor shaft self of screw compressor become greatly, for example become the vibration of the allowable load that exceedes bearing such, need to self take some vibration countermeasure to the rotor shaft of screw compressor.It should be noted that, rotor shaft self is being implemented to vibration countermeasure in the situation that, the research of having to make an effort is so that the unbalanced force (unbalanced force) of this vibration countermeasure while not acting as the rotation of rotor shaft.
In addition, outstanding be arranged on the clava on motor case and be inserted in the such structure of the plate (mass body) of this claval displacement along the vertical direction, the space that need to guarantee to configure clava and plate (mass body) in the outside of motor case, the assembly layout of compressor is restricted sometimes.In addition, obtaining thermal equilibrium is also restricted.
Summary of the invention
The present invention proposes in view of above-mentioned actual conditions, its object is to provide a kind of cantilevered motor direct linkage type screw compressor that possesses vibration damping structure, directly reduces the vibration of rotor shaft self when unbalanced force (unbalanced force) when rotation that this vibration damping structure can be difficult for producing rotor shaft.
In order to reach above-mentioned purpose, the invention provides a kind of screw compressor, it possesses: helical rotor; Screw axis, it is coaxial and become one structure with respect to this male rotor with the male rotor of described helical rotor; Spiral-shell, it accommodates described helical rotor and described screw axis; Motor reel, it is coaxial and become one structure with respect to this screw axis with described screw axis, and in helical rotor side by cantilever support; Motor, it makes described motor reel rotation; Weight, it is with can be along the axially movable state of described motor reel and roughly arranged coaxial of this motor reel, described electric tools is standby be fixed on described motor reel periphery rotor, be configured in described rotor outside stator, accommodate the motor case of described rotor and described stator, the axially-displaceable momentum of described weight is larger than the movable amount on the axle orthogonal direction of this weight.
In this structure, be in the screw axis and the motor reel that are integrated suitable with " rotor shaft being rotated ".According to said structure, with respect to the flexure vibrations of rotor shaft, such as, because the stroke end (axle head of motor reel) before and after axial etc. causes vibrational energy consumption (consumption of the vibrational energy that axial impact causes) with weight collision etc., consequently, the vibration of rotor shaft reduces.
In addition, by by roughly arranged coaxial and make the axially-displaceable momentum of weight larger than the movable amount on the axle orthogonal direction of this weight of weight and motor reel, thus the unbalanced force (unbalanced force) when the rotation that can be difficult for producing rotor shaft and improve axial impact etc. and consume the consumption efficiency of vibrational energies.
In addition, in the present invention, preferred described screw compressor also possesses bar-shaped by slide member, this is bar-shaped coaxial and be fixed on this motor reel with described motor reel by slide member, and the diameter of axle is less than the diameter of axle of this motor reel, the described weight of ring-type is loosely inserted into described bar-shaped by slide member.
According to this structure, the weight that makes ring-type by employing with respect to the bar-shaped mode of loosely being inserted by slide member of motor arranged coaxial, thereby the unbalanced force (imbalance) when the rotation of more difficult generation rotor shaft.
And then, in the present invention, the motor side end face of preferred described motor reel is configured in the position by helical rotor side than the motor side end face of described rotor, described screw compressor possesses coaxial with described motor reel and is fixed on the end component of the motor side end face of described rotor, and described weight is accommodated in the space between motor side end face and the described end component of described motor reel.
According to this structure, accommodate weight by the space between motor side end face and described end component at motor reel, can make thus the axial length of screw compressor entirety compared with prior art roughly the same.
In addition, become large part, i.e. the end configuration weight of the opposition side of the cantilever support side of motor reel in the flexure vibrations of rotor shaft.,, according to said structure (weight configuration), can further improve the consumption efficiency of the consumption vibrational energies such as axial impact.
And then in the present invention, preferred described screw compressor possesses coaxial with described motor reel and is fixed on the end component of the motor side end face of described rotor, configures described weight in the outside of described end component.
According to this structure, can in the situation that not pulling down end component, settle weight.In addition, in the time of the quantity adjustment etc. of carrying out weight, the space utilization in the outside of the end component in motor case can be made to the configuration space of weight, not need to carry out the processing (length of motor reel changes) of motor reel etc.
In addition, becoming large part, i.e. the position configuration weight in the outer part of end of the opposition side of the cantilever support side of motor reel than the flexure vibrations of rotor shaft.,, according to said structure (weight configuration), can further improve the consumed power of the consumption vibrational energies such as axial impact.
And then, in the present invention, the bulk material of preferably enclosing toughness body or vibrating along with the vibration of described motor reel in described space.
According to this structure, by enclosing toughness body, can produce viscous damping at the slip surface of weight, consequently, also can reduce the vibration of rotor shaft by this viscous damping.In addition, if enclose bulk material, the frictional attenuation producing by the interparticle friction of bulk material also can reduce the vibration of rotor shaft.
It should be noted that, as viscous body, the preferably high viscous body of viscosity of 10000cSt～100000cSt degree.In addition, as bulk material, the preferably bulk material of the particle diameter of 100 μ m～a few mm degree.
And then, in the present invention, preferably in described space, contain elastomer and the decay body that supports vertically described weight or the viscoelastic body that supports vertically described weight.
According to this structure, vibrate vertically with respect to the vibration weight of rotor shaft, thus the vibrational energy that consumes rotor shaft by its reaction force., reduce the vibration of rotor shaft by the damping effect of so-called dynamic vibration absorber.It should be noted that, as elastomer, that can enumerate that the materials such as the spring such as leaf spring of helical spring and convex and rubber, plastics form has a flexible elastomer etc.
And then, in the present invention, preferably support vertically the elastomer of described weight and the decay body of ring-type or support vertically described weight ring-type viscoelastic body be loosely inserted into described bar-shaped by the state configuration on slide member the outside at described end component.
According to this structure, vibrate vertically with respect to the vibration weight of rotor shaft, thus the vibrational energy that consumes rotor shaft by its reaction force., reduce the vibration of rotor shaft by the damping effect of so-called dynamic vibration absorber.It should be noted that, as elastomer, that can enumerate that the materials such as the spring such as leaf spring of helical spring and convex and rubber, plastics form has a flexible elastomer etc.
And then in the present invention, preferably at least either side in the axial both sides of described weight is configured for the spacer element of the axially-displaceable momentum of adjusting this weight.
According to this structure, under the effect of above-mentioned spacer element, the unbalanced force (imbalance) when the difficult rotation that produces rotor shaft.
And then, in the present invention, preferably have vertically and with the orthogonal direction of axle in the multiple described weight of at least any direction disposed adjacent.
According to this structure, also can consume vibrational energy by weight axial impact each other.In addition, if increase the quantity (if weight is made to multi-layer structure) of weight, the vibration area of weight also increases, and is easier to consume vibrational energy.
Invention effect
According to the present invention, by by weight can being roughly configured in coaxially described motor side along the axially movable state of motor reel and this motor reel, thus with respect to the flexure vibrations of rotor shaft (being in the screw axis and the motor reel that are structure as a whole), stroke ends axially etc. consume vibrational energy with weight collision, thereby reduce the vibration of rotor shaft.Under the effect of this weight, the unbalanced force (unbalanced force) when the rotation that can be difficult for producing rotor shaft, can directly reduce the vibration of the rotor shaft self of rotation simultaneously.
Accompanying drawing explanation
Fig. 1 is that the side that represents the related screw compressor of the first mode of execution of the present invention is cutd open schematic diagram.
Fig. 2 is A portion enlarged view and the X-X sectional drawing thereof of Fig. 1.
Fig. 3 is that the side that represents the related screw compressor of the second mode of execution of the present invention is cutd open schematic diagram.
Fig. 4 is B portion enlarged view and the Y-Y sectional drawing thereof of Fig. 3.
Fig. 5 is that the side that represents the related screw compressor of the 3rd mode of execution of the present invention is cutd open schematic diagram.
Fig. 6 is C portion enlarged view and the Z-Z sectional drawing thereof of Fig. 5.
Fig. 7 is that schematic diagram is cutd open in the local Zoom Side that represents the related screw compressor of the 4th mode of execution of the present invention.
Fig. 8 is that schematic diagram is cutd open in the local Zoom Side of the variation of the screw compressor shown in presentation graphs 1 and Fig. 2.
Fig. 9 is that schematic diagram is cutd open in the local Zoom Side of the variation of the screw compressor shown in presentation graphs 5 and Fig. 6.
Figure 10 is that schematic diagram is cutd open in the local Zoom Side that represents the related screw compressor of the 5th mode of execution of the present invention.
Figure 11 is that schematic diagram is cutd open in the local Zoom Side that represents the variation of the screw compressor shown in Figure 10.
Figure 12 is that schematic diagram is cutd open in the local Zoom Side that represents the related screw compressor of the 6th mode of execution of the present invention.
Symbol description:
1 screw compressor
2 helical body portions
3 screw axis
4 helical rotors
4a male rotor
5 rotors
6 stators
7 motor reels
8 weights
9 bolts (bar-shaped by slide member)
10 end components
12 spiral-shells
13 motor cases
30 motor part (motor)
Embodiment
Below, with reference to the accompanying drawings of for implementing mode of the present invention.
(the first mode of execution)
Fig. 1 is that the side that represents the related screw compressor 1 of the first mode of execution of the present invention is cutd open schematic diagram.Fig. 2 is A portion enlarged view (Fig. 2 (a)) and the X-X sectional drawing (Fig. 2 (b)) thereof of Fig. 1.
(structure of screw compressor)
As shown in Figure 1, screw compressor 1 is to possess helical body portion 2 and motor part 30 (motor) and the screw compressor of the motor direct coupled structure that forms.
(helical body portion)
Helical body portion 2 has a pair of helical rotor 4 of negative and positive, with the male rotor 4a screw axis 3 coaxial and that become one structure with respect to male rotor 4a of helical rotor 4, accommodate the spiral-shell 12 of helical rotor 4 and screw axis 3.Screw axis 3 is by bearing 14 and bearing 15 cantilever support.
The male rotor 4a of helical rotor 4 and screw axis 3 are made by steel being cut out to processing etc.In addition also can independently make respectively after male rotor 4a and screw axis 3 both rigidity links (one link).In addition, thus screw axis 3 make and become one structure by steel being cut out to processing etc. together with motor reel 7 described later.By the rotor shaft 11 that is in the screw axis 3 that is structure as a whole and motor reel 7 and forms rotation.In addition, both rigidity are linked to (one link) after also screw axis 3 and motor reel 7 independently can being made respectively.Link as rigidity that the method for (integrative-structure) is known has flange to link.
(motor part)
Motor part 30 (motor) is the driving source for rotor shaft 11 is rotated, have the periphery that is fixed on motor reel 7 rotor 5, be fixed on the outside of rotor 5 stator 6, accommodate the motor case 13 of rotor 5 and stator 6.Motor reel 7 is coaxial and become one structure with respect to screw axis 3 with screw axis 3, and by helical rotor 4 side cantilever support.Particularly, by bearing 14 (and bearing 15) the cantilever support motor reel 7 of helical rotor 4 sides.
The motor side end face 7a of motor reel 7 is positioned at the position by helical rotor 4 sides than the motor side end face 5a of rotor 5.Motor side end face 5a at rotor 5 is fixed with discoideus end component 10 by bolt (not shown) etc.Parts 10 offers at center porose endways.End component 10 is coaxial with motor reel 7.
(bar-shaped by slide member and weight)
Motor side end face 7a at motor reel 7 is fixed with bolt 9 with motor reel 7 coaxial (at the rotating center of motor reel 7).Bolt 9 is involved in the present invention bar-shaped by an example of slide member.
(bar-shaped by slide member and weight)
Motor side end face 7a at motor reel 7 is fixed with bolt 9 with motor reel 7 coaxial (at the rotating center of motor reel 7).Bolt 9 is of the present invention bar-shaped by an example of slide member.
As shown in Fig. 2 (a), bolt 9 is by being formed by slip axial region 16 and head 17 (large-diameter portion), this is fixed on the motor side end face 7a of motor reel 7 to be formed through the mode of the hole 10a at parts 10 center endways by the axial region 16 that slides, this head 17 is formed on by one 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 reel 7 by the diameter of axle of slip axial region 16.
Here, the weight 8 of multiple ring-types is housed in the space between motor side end face 7a and the end component 10 of motor reel 7 to be loosely inserted into the state by slip axial region 16 of bolt 9.Like this, become can be along the axially movable state of motor reel 7 for weight 8.In the present embodiment, having six weights 8, but be not limited to six, can be also one.
In addition, being circular, but also need not be circle by the sectional shape of slip axial region 16, for example, can be also quadrilateral etc.Be formed on weight 8 center hole 8a too, differ and be decided to be circle, can be also for example quadrilateral etc.Be formed on the shape of hole 8a at the center of weight 8 with consistent by the sectional shape of slip axial region 16.In addition, the sectional shape of head 17 need not be Hexagon, for example, can be also circle etc.
(configuration of weight)
The axially-displaceable momentum of weight 8 is set as larger than the movable amount with in the orthogonal direction of axle of this weight 8.Here, the thickness of every a slice weight 8 is tmm, the motor side end face 7a of motor reel 7 and end component 10 be spaced apart Lmm.The axially-displaceable momentum of weight 8 is defined by (L-t × weight number)/2.The axially-displaceable momentum of weight 8 is for example about 0.5mm～several mm.
Be d1mm by the diameter of axle of slip axial region 16, the internal diameter of weight 8 is d2mm, the outside diameter d 3mm of weight 8, and the internal diameter of rotor 5 is d4mm.Weight 8 with the orthogonal direction of axle on movable amount by value definition smaller in (d2-d1)/2 and (d4-d3)/2.The movable amount with in the orthogonal direction of axle of weight 8 is set as and the same degree of chimeric size of rotor 5 and stator 6, for example, be made as about 0.02mm～approximately 0.5mm.In addition, as previously mentioned, the movable amount with in the orthogonal direction of axle of the axially-displaceable momentum proportion thing 8 of weight 8 large (in other mode of executions, variation too).That is, by weight 8 with the orthogonal direction of axle on movable amount while being set as larger value, for example 0.5mm, the axially-displaceable momentum of weight 8 is set to such an extent that be greater than 0.5mm.
Here,, in Fig. 2 (a), weight 8 is illustrated as coaxial with motor reel 7.But, weight 8 is loosely being inserted into by slip axial region 16 and under static state of bolt 9, strictly speaking, the axle center that becomes weight 8 than the axle center of motor reel 7 along vertical direction declined described weight 8 with the orthogonal direction of axle on the state of movable amount (0.02mm～0.5mm left and right).That is, in the present invention, with motor reel 7 " roughly " arranged coaxial weight 8 show become the axle center of weight 8 than the axle center of motor reel 7 along the declined state of the movable amount in the orthogonal direction of itself and axle of vertical direction.
In addition, in the present embodiment, dispose weight 8 near the opposition side end (end component 10) of the cantilever support side of motor reel 7, but the allocation position of weight 8 is not limited to this.For example, also can the middle part of rotor shaft 11 divide form the diameter of axle be less than this rotor shaft 11 the diameter of axle bar-shaped by slide part and this partial relaxation insert weight 8.
(effect)
According to the screw compressor 1 of present embodiment, with respect to the flexure vibrations of the rotor shaft 11 mainly causing because of the rotation of helical rotor 4, stroke end (the motor side end face 7a of motor reel 7 and the end face of end component 10) axially conflicts with weight and consumes vibrational energy (consumption of the vibrational energy that axial impact causes), consequently, the vibration of rotor shaft 11 reduces., directly reduce the vibration of the rotor shaft 11 self of rotation by moving vertically the weight 8 colliding.In addition, by becoming large part, i.e. near opposition side end (end component 10) the configuration weight 8 of the cantilever support side of motor reel 7 in the flexure vibrations of rotor shaft 11, can further improve thus axial impact the consumed power that consumes vibrational energy.
In addition, by with motor reel 7 arranged coaxial weights 8 and make the axially-displaceable momentum of weight 8 be greater than the movable amount in the orthogonal direction of itself and axle, can be difficult for producing thus rotor shaft 11 rotation time unbalanced force (unbalanced force), and can improve axial impact and consume the consumed power of vibrational energy.In addition, the weight 8 that makes ring-type by employing is with respect to the mode of loosely inserting with the bolt 9 of motor reel 7 arranged coaxial, thus the unbalanced force (imbalance) when the rotation that is difficult for producing rotor shaft 11.
And then, dispose multiple weights 8 due to adjacent vertically, therefore can consume vibrational energy by weight 8 axial impact each other.
In addition, accommodate weight by the space between motor side end face 7a and end component 10 at motor reel 7, can make the axial length of screw compressor entirety and existing equipment roughly the same.
(the second mode of execution)
Fig. 3 is that the side that represents the related screw compressor 102 of the second mode of execution of the present invention is cutd open schematic diagram.Fig. 4 is B portion enlarged view (Fig. 4 (a)) and the Y-Y sectional drawing (Fig. 4 (b)) thereof of Fig. 3.In Fig. 3 and Fig. 4, the parts identical with parts in the screw compressor 1 of the first mode of execution are marked to identical symbol.
The screw compressor 1 of the first mode of execution is with the main difference point of the screw compressor 102 of present embodiment, and the screw compressor 102 of present embodiment possesses the spacer element 18 of tubular.
(spacer element)
Here,, during by the length setting umm of spacer element 18, the axially-displaceable momentum of weight 8 is defined by (L-t × weight number-u × interval number of packages)/2.The axially-displaceable momentum of weight 8 is for example about 0.5mm～several mm.
The internal diameter of spacer element 18 is set as the d2mm identical with the internal diameter of weight 8.The movable amount with in the orthogonal direction of axle by the spacer element 18 of (d2-d1)/2 definition is set as and the same degree of chimeric size of rotor 5 and stator 6, for example, be made as about 0.02mm～approximately 0.5mm.In addition, the hole 18a being formed centrally in spacer element 18 is not limited to circle, for example, can be also quadrilateral etc.The shape of the hole 18a being formed centrally in spacer element 18 is with consistent by the sectional shape of slip axial region 16.
(effect)
If the axially-displaceable momentum of weight 8 is excessive, thereby weight 8 moves and produces the unbalanced force (unbalanced force) of rotor shaft 11 while rotating in the mode of for example toppling over.Adjust the axially-displaceable momentum of weight 8 by spacer element 18, can prevent thus toppling over of weight 8, and unbalanced force (unbalanced force) while being difficult for producing the rotation of rotor shaft 11.
(the 3rd mode of execution)
Fig. 5 is that the side that represents the related screw compressor 103 of the 3rd mode of execution of the present invention is cutd open schematic diagram.Fig. 6 is C portion enlarged view (Fig. 6 (a)) and the Z-Z sectional drawing (Fig. 6 (b)) thereof of Fig. 5.In Fig. 5 and Fig. 6, the parts identical with the parts of the screw compressor 1 of the first mode of execution are marked to identical symbol.
The main difference point of the screw compressor 1 of the first mode of execution and the screw compressor 103 of present embodiment is the configuration of weight, in the screw compressor 103 of present embodiment, weight is configured in than end component 10 position in (the axial outside of rotor 5) in the outer part.
(bar-shaped by slide member and weight)
The bolt 21 (bar-shaped by slide member) of present embodiment is by being formed by slip axial region 22 and head 23 (large-diameter portion), this is fixed on the motor side end face 7a of motor reel 7 to be formed through the mode of the hole 10a at parts 10 center endways by the axial region 22 that slides, this head 23 is formed on by one end of slip axial region 22.There is in order minor diameter part 22a, the 22b of central diameter portion by slip axial region 22 from the end face side of motor reel 7.The external diameter of head 23 is greater than by the diameter of axle of the minor diameter part 22a of slip axial region 22, the 22b of central diameter portion, and is greater than the internal diameter of weight 20.By making the external diameter of head 23 be greater than the internal diameter of weight 20, weight 20 can not fly out and come off from the end of bolt 21 thus.
The head 23 of bolt 21 is positioned at than end component 10 in the outer part, in other words, is positioned at the position in the axial outside of rotor 5.The sectional shape of head 23 is Hexagon, but need not be Hexagon, also can be for for example circular etc.
And, the weight 20 that is loosely inserted multiple ring-types by the 22b of central diameter portion of slip axial region 22 between head 23 and the end component 10 of bolt 21.In the present embodiment, weight 20 is three, but is not limited to three, can be one.
The axially-displaceable momentum of weight 20 is set as larger than the movable amount in the orthogonal direction of itself and axle.Here, the thickness of every a slice weight 20 is tmm, the head 23 of bolt 21 and the L2mm that is spaced apart of end component 10.The axially-displaceable momentum of weight 20 is defined by (L2-t × weight number)/2.The axially-displaceable momentum of weight 20 is for example about 0.5mm～several mm.
Be d1mm by the diameter of axle of the minor diameter part 22a of slip axial region 22, the diameter of axle of the 22b of central diameter portion is d2mm, and the internal diameter of weight 20 is d3mm, and the external diameter of head 23 is d4mm, the outside diameter d 5mm of weight 20.The movable amount with in the orthogonal direction of axle of weight 20 is defined by (d3-d2)/2.The movable amount with in the orthogonal direction of axle of weight 20 is set as and the same degree of chimeric size of rotor 5 and stator 6, for example, be made as about 0.02mm～approximately 0.5mm.
(effect)
According to the screw compressor 103 of present embodiment, become large part in the flexure vibrations of rotor shaft 11, than the opposition side end of the cantilever support side of motor reel 7 position configuration weight 8 in the outer part, can further improve axial impact and consume the consumption efficiency of vibrational energy.In addition, according to screw compressor 103, can in the situation that not pulling down end component 10, settle weight 8.In addition, while carrying out the quantity adjustment etc. of weight 8, substantially only change the length of the 22b of central diameter portion of bolt 21, do not need to carry out the processing (length of motor reel 7 changes) of motor reel 7 etc.In addition, the outside dimension of weight 8 also can be determined arbitrarily.
(embodiment)
Make testing installation for the screw compressor 1 that disposes weight 8 in the inner side of rotor 5, vibrate and reduce effect validation test.Test conditions and test result are as shown in table 1 below.It should be noted that, the symbol that table 1 is recorded is consistent with Fig. 2 (a).According to this test, can confirm that vibration reduces effect fully.
[table 1]
Make experimental facilities for the screw compressor 102 that disposes spacer element 18 in the inner side of rotor 5, carried out vibration and reduced effect validation test.Test conditions and test result are as shown in table 2 below.It should be noted that, the symbol that table 2 is recorded is consistent with Fig. 4 (a).According to this test, can confirm that vibration reduces effect fully.
[table 2]
Make experimental facilities for the screw compressor 103 that disposes spacer element 20 in the axial outside of rotor 5, vibrate and reduce effect validation test.Test conditions and test result are as shown in table 3 below.It should be noted that, the symbol that table 3 is recorded is consistent with Fig. 6 (a).According to this test, can confirm that vibration reduces effect fully.
[table 3]
(the 4th mode of execution)
Fig. 7 is that schematic diagram is cutd open in the local Zoom Side of the related screw compressor of four embodiment of the invention 104, is the figure suitable with the local Fig. 2 (a) that represents screw compressor 1.In Fig. 7, the parts identical with parts in the screw compressor 1 of the first mode of execution are marked to identical symbol.
In the present embodiment, the space between parts 10 and motor side end face 7a not only disposes weight 8 endways, also encloses toughness body 24.By enclosing toughness body 24, can produce viscous damping at the slip surface of weight 8, consequently, also can reduce the vibration of motor reel 11 by this viscous damping.Here, the slip surface of weight 8 refers to face that weight 8 and the face being joined by slip axial region 16, weight 8 and rotor 5 join etc.In addition,, as viscous body 24, can enumerate lubricating grease, silicone oil etc. that viscosity is high.The preferably viscous body 24 of the viscosity of 10000cSt～100000cSt degree.
As the variation of the 4th mode of execution, also preferably the bulk material vibrating along with the vibration of motor reel 7 is enclosed in the space between parts 10 and motor side end face 7a endways.If inclosure bulk material, the frictional attenuation producing by the interparticle friction of bulk material also can reduce the vibration of rotor shaft 11.In addition, as bulk material, can enumerate reduced iron particle and sintered steel, the Shirasuballoon (the fine hollow glass ball forming take volcanic ash as raw material) of glass system and the bulk material of pottery system etc. of slag (blast furnace slow cool down slag, blast furnace granulated slag, vessel slag, electroslag etc.), cold rolling particle (utilizing adhesive that iron powder dust pulverized fuel ash etc. is frozen into the material that granular forms), metal system.The preferably bulk material of the particle diameter of 100 μ m～a few mm degree.
(variation)
Fig. 8 is that schematic diagram is cutd open in the local Zoom Side of the variation of the screw compressor 1 shown in presentation graphs 1 and Fig. 2, and arbitrary figure is the figure suitable with the local Fig. 2 (a) that represents screw compressor 1.
Not only along the multiple weights of axial disposed adjacent of motor reel 7, as shown in Fig. 8 (a), also along motor reel 7 with the orthogonal multiple weights 25,26 of direction (radially) disposed adjacent of axle.The internal diameter of the weight 25 of ring-type is larger than the internal diameter of the weight of ring-type 26.By along motor reel 7 with orthogonal direction (radially) disposed adjacent (multi-layer configuration) weight 25,26 of axle, weight 25,26 also slides each other thus, the slide area of weight increases, and is therefore easy to further consume vibrational energy.
In addition,, in the manner, preferably viscous body 24 or the bulk material shown in Fig. 7 enclosed in the space between parts 10 and motor side end face 7a endways.By enclosing toughness body 24, also produce viscous damping at the slip surface of 25,26, weight.By enclosing bulk material, the particle that also can obtain bulk material on 25,26, weight rubs and the frictional attenuation effect that produces each other.In addition, in the manner, along having two weights 25,26 with the orthogonal direction disposed adjacent (multi-layer configuration) of axle, but also can along with more than three weight of the orthogonal direction disposed adjacent (multi-layer configuration) of axle.
In addition, as shown in Fig. 8 (b), also the space between parts 10 (there is no hole) and motor side end face 7a configures multiple discoideus weights 27 that there is no hole endways., also can omit the bolt 9 shown in Fig. 2 (a).According to the manner, collide and consume vibrational energy by stroke end (the motor side end face 7a of motor reel 7 and the end face of end component 10) and the weight 27 of axial front and back, the vibration of rotor shaft 11 reduces thus.In addition, by with the roughly discoideus weight 27 of arranged coaxial and make the axially-displaceable momentum of weight 27 be greater than the movable amount in the orthogonal direction of itself and axle, the unbalanced force (unbalanced force) when the rotation that can be difficult for producing thus rotor shaft 11 of motor reel 7.
Next, Fig. 9 is that schematic diagram is cutd open in the local Zoom Side of the variation of the screw compressor 103 shown in presentation graphs 5 and Fig. 6, and arbitrary figure is the figure suitable with the local Fig. 6 (a) that represents screw compressor 103.
As shown in Fig. 9 (a), also the outside of parts 10 endways, not only along the axial disposed adjacent weight 28,29 of motor reel 7, also along motor reel 7 with orthogonal direction (radially) disposed adjacent (multi-layer configuration) weight 28,29 of axle.Thus, because weight 28,29 also slides each other, therefore the slide area of weight also increases, and is easy to further consume vibrational energy.In addition,, the in the situation that of the manner, between the head 23 of bolt 21 and weight 28,29, dispose the spacer element 31 of discoideus (porose), so that the weight 29 of radial outside does not fly out and comes off from the end of bolt 21.This spacer element 31 is for adjusting the axially-displaceable momentum of weight 28,29.
In addition, also can, as shown in Fig. 9 (b), two weights of motor side in three weights 20 shown in Fig. 6 (a) be divided into respectively to weight 28 and weight 29.According to which, do not need the spacer element 31 shown in Fig. 9 (a).
(the 5th mode of execution)
Figure 10 is that schematic diagram is cutd open in the local Zoom Side of the related screw compressor 105 of the 5th mode of execution of the present invention, is the figure suitable with the local Fig. 2 (a) that represents screw compressor 1.In Figure 10, the parts identical with parts in the screw compressor 1 of the first mode of execution are marked to identical symbol (in Figure 11 described later too).
In the present embodiment, the space between parts 10 and motor side end face 7a disposes the decay body 33 of the weight 19 of a ring-type, two helical springs 32, two ring-types endways.The state configuration that two helical springs 32 are inserted into decay body 33 with the outside of the decay body 33 from ring-type is the space between parts 10 and motor side end face 7a endways.And then two helical springs 32 are respectively charged between end component 10 and weight 19 under compressed state, between weight 19 and motor side end face 7a.Like this, the weight 19 of ring-type is supported vertically by helical spring 32 and decay body 33.In addition, same with the weight 8 of the first mode of execution, unbalanced force (unbalanced force) when making the same degree of chimeric size of the outer circumferential face of weight 19 and the inner peripheral surface of the chimeric size of rotor 5 or weight 19 and the chimeric size of bolt 9 and rotor 5 and stator 6, can be difficult for thus producing rotor shaft 11 to rotate.Here,, as decay body 33, can enumerate for example silicon is gelatinous decay body.
According to present embodiment, vibrate vertically with respect to the vibration weight 10 of rotor shaft 11, thus the vibrational energy that consumes rotor shaft 11 by its reaction force.,, when unbalanced force (unbalanced force) when the rotation that can be difficult for producing rotor shaft 11, directly reduce the vibration of rotor shaft 11 by the damping effect of so-called dynamic vibration absorber.
As the variation of the 5th mode of execution, also can be as shown in Figure 11 (a), replace helical spring 32 to use the convex leaf spring 35 of ring-type.In addition, also can replace the decay body 33 of ring-type and the viscous bodies 34 such as lubricating grease high viscosity are enclosed to the space between end component 10 and motor side end face 7a.As viscous body 34, except the high lubricating grease of viscosity, can also enumerate silicone oil etc.The preferably annual viscous body 34 of 1000cSt～10000cSt degree.
In addition, also can be as shown in Figure 11 (b), replace helical spring 32 and decay body 33, and endways between parts 10 and weight 19 and configure the viscoelastic body 36 of ring-type between weight 19 and motor side end face 7a, thereby prop up vertically load-bearing material 19 by this viscoelastic body 36.As viscoelastic body 36, the preferably height of service wear rate 0.2～0.5 degree decay rubber (for example, butyl is rubber).In addition, in this variation, dispose multiple viscoelastic bodies 36 in the both sides of weight 19, but also can be at viscoelastic body 36 of the both sides of the weight 19 each configuration of difference.
And then, although omitted diagram, also can the weight 27 shown in Fig. 8 (b), weight 19, decay body 33 and viscous body 34 are formed as not having to the form in hole, and omit bolt 9.
And then, for example, in the damper mechanism shown in Figure 10, also only the one-sided configuration helical spring 32 in the both sides of weight 19 and decay body 33 (in Figure 11, Figure 12 too).Consume vibrational energy in a side that does not configure helical spring 32 and decay body 33 by weight 19 and end component 10 (or axle head of motor reel 7) collision.
(the 6th mode of execution)
Figure 12 (a) is that schematic diagram is cutd open in the local Zoom Side of the related screw compressor of sixth embodiment of the invention 106, is the figure suitable with the local Fig. 6 (a) that represents screw compressor 103.In Figure 12 (a), the parts identical with parts in the screw compressor 103 of the 3rd mode of execution are marked to identical symbol (in Figure 12 described later (b) too).
In the present embodiment, with the state that is loosely inserted into bolt 21, the decay body 38 of the weight of a ring-type 37, two helical springs 39, two ring-types is configured in to the outside of end component 10 and is configured between the head 23 and end component 10 of bolt 21.The state configuration that two helical springs 39 are inserted into decay body 38 with the outside of the decay body 38 from ring-type is between the head 23 and end component 10 of bolt 21.And then two helical springs 39 are respectively charged between the head 23 and weight 37 of bolt 21 under compressed state, between weight 37 and end component 10.Like this, the weight 37 of ring-type is supported vertically by helical spring 39 and decay body 38.In addition, same with the weight 20 of the 3rd mode of execution, by making the same degree of chimeric size of the inner peripheral surface of weight 37 and the chimeric size of bolt 21 and rotor 5 and stator 6, the unbalanced force (unbalanced force) can be difficult for thus producing rotor shaft 11 and rotate time.Here,, as decay body 38, can enumerate for example silicon is gelatinous decay body.
According to present embodiment, vibrate vertically with respect to the vibration weight 37 of rotor shaft 11, thus the vibrational energy that consumes rotor shaft 11 by its reaction force., the unbalanced force (unbalanced force) when the rotation that can be difficult for producing rotor shaft 11, directly reduces the vibration of rotor shaft 11 by the damping effect of so-called dynamic vibration absorber.In addition, although the diagram of omission also can replace helical spring 39 with the convex leaf spring 35 of the ring-type shown in Figure 11 (a).
In addition, as the variation of the 6th mode of execution, also can be as shown in Figure 12 (b), replace helical spring 39 and decay body 38, between the head 23 of bolt 21 and end component 10, configure the viscoelastic body 40 of ring-type, thereby prop up vertically load-bearing material 37 by this viscoelastic body 40.As viscoelastic body 40, the preferably height of service wear rate 0.2～0.5 degree decay rubber (for example butyl rubber).In addition, in variation, dispose multiple viscoelastic bodies 40 in the both sides of weight 37, but also can be at viscoelastic body 40 of the both sides of the weight 37 each configuration of difference.
Above, embodiments of the present invention are illustrated, but the present invention is not limited to above-mentioned mode of execution, in the scope that can record at claims, implements various changes.For example, mode of execution shown in can appropriately combined Fig. 1～Figure 12 and implementing.
Claims (10)
1. a screw compressor, is characterized in that, possesses:
Helical rotor;
Screw axis, it is coaxial and become one structure with respect to this male rotor with the male rotor of described helical rotor;
Spiral-shell, it accommodates described helical rotor and described screw axis;
Motor reel, it is coaxial and become one structure with respect to this screw axis with described screw axis, and in helical rotor side by cantilever support;
Motor, it makes described motor reel rotation;
Weight, it is with can be along the axially movable state of described motor reel and roughly arranged coaxial of this motor reel,
Described electric tools is standby be fixed on described motor reel periphery rotor, be configured in described rotor outside stator, accommodate the motor case of described rotor and described stator,
The axially-displaceable momentum of described weight is larger than the movable amount on the axle orthogonal direction of this weight,
Stroke end and the collision of described weight by axial front and back consume vibrational energy.
2. screw compressor according to claim 1, is characterized in that,
Also possess bar-shapedly by slide member, this is bar-shaped coaxial and be fixed on this motor reel with described motor reel by slide member, and the diameter of axle is less than the diameter of axle of this motor reel,
The described weight of ring-type is loosely inserted into described bar-shaped by slide member.
3. screw compressor according to claim 1, is characterized in that,
The motor side end face of described motor reel is configured in the position by helical rotor side than the motor side end face of described rotor,
Described screw compressor possesses coaxial with described motor reel and is fixed on the end component of the motor side end face of described rotor,
Described weight is accommodated in space between motor side end face and the described end component of described motor reel.
4. screw compressor according to claim 2, is characterized in that,
The motor side end face of described motor reel is configured in the position by helical rotor side than the motor side end face of described rotor,
Described screw compressor possesses coaxial with described motor reel and is fixed on the end component of the motor side end face of described rotor,
Described weight is accommodated in space between motor side end face and the described end component of described motor reel.
5. screw compressor according to claim 2, is characterized in that,
Possess coaxial with described motor reel and be fixed on the end component of the motor side end face of described rotor,
Configure described weight in the outside of described end component.
6. according to the screw compressor described in claim 3 or 4, it is characterized in that,
In described space, contain elastomer and the decay body that supports vertically described weight or the viscoelastic body that supports vertically described weight.
7. screw compressor according to claim 5, is characterized in that,
Support vertically the elastomer of described weight and the decay body of ring-type or support vertically described weight ring-type viscoelastic body be loosely inserted into described bar-shaped by the state configuration on slide member the outside at described end component.
8. according to the screw compressor described in any one in claim 1～5, it is characterized in that,
At least either side in the axial both sides of described weight is configured for the spacer element of the axially-displaceable momentum of adjusting this weight.
9. according to the screw compressor described in any one in claim 1～5, it is characterized in that,
Have vertically and with the orthogonal direction of axle in the multiple described weight of at least any direction disposed adjacent.
10. screw compressor according to claim 8, is characterized in that,
Have vertically and with the orthogonal direction of axle in the multiple described weight of at least any direction disposed adjacent.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2010043319 | 2010-02-26 | ||
| JP2010-043319 | 2010-02-26 | ||
| JP2010173876A JP5307775B2 (en) | 2010-02-26 | 2010-08-02 | Screw compressor |
| JP2010-173876 | 2010-08-02 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102168675A CN102168675A (en) | 2011-08-31 |
| CN102168675B true CN102168675B (en) | 2014-06-18 |
Family
ID=44489957
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201110042120.4A Active CN102168675B (en) | 2010-02-26 | 2011-02-17 | Spial compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN102168675B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5500558B2 (en) * | 2011-10-05 | 2014-05-21 | 株式会社神戸製鋼所 | Screw compressor |
| JP5683426B2 (en) * | 2011-10-05 | 2015-03-11 | 株式会社神戸製鋼所 | Screw compressor |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1222645A (en) * | 1997-11-28 | 1999-07-14 | 株式会社丰田自动织机制作所 | Compressor |
| CN101178066A (en) * | 2006-11-10 | 2008-05-14 | 日立空调·家用电器株式会社 | Hermetic screw compressor |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001124111A (en) * | 1999-10-26 | 2001-05-08 | Nok Vibracoustic Kk | Coupling for electromagnetic clutch |
| JP2001241508A (en) * | 2000-02-25 | 2001-09-07 | Nok Vibracoustic Kk | Coupling for electromagnetic clutch |
| JP4190803B2 (en) * | 2002-05-23 | 2008-12-03 | 株式会社神戸製鋼所 | Vibration control device |
-
2011
- 2011-02-17 CN CN201110042120.4A patent/CN102168675B/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1222645A (en) * | 1997-11-28 | 1999-07-14 | 株式会社丰田自动织机制作所 | Compressor |
| CN101178066A (en) * | 2006-11-10 | 2008-05-14 | 日立空调·家用电器株式会社 | Hermetic screw compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102168675A (en) | 2011-08-31 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN106461012B (en) | Centrifugal force pendulum | |
| US6448679B1 (en) | Passive magnetic support and damping system | |
| CN102893055B (en) | Torque transmission assembly and drive system with torque transmission assembly | |
| CN102278308B (en) | Screw compressor | |
| CN102168675B (en) | Spial compressor | |
| JP2017523347A (en) | Rotary screw compressor using viscous damping for vibration reduction | |
| JP2008101769A (en) | Vibration reducing mechanism and its specification setting method | |
| CN105465272A (en) | Torsion damper | |
| CN103590320B (en) | A kind of vibration absorbing device for staying cables of bridge of cable-stayed bridge | |
| CN103032324B (en) | Screw compressor | |
| CN100417836C (en) | Device and method for damping vibration of rotating shaft system | |
| JP5307775B2 (en) | Screw compressor | |
| CN109458426B (en) | Vibration isolator | |
| CN100510459C (en) | Damp self-compensated ball-hinge type back/top frame vibration-isolator | |
| CN103032325B (en) | Screw compressor | |
| JP4190803B2 (en) | Vibration control device | |
| KR20130004782A (en) | Propeller shaft having damping function | |
| JP2000500554A (en) | Magnetic bearing | |
| CN208966935U (en) | A kind of dynamic vibration absorber and vehicle | |
| KR101202569B1 (en) | Dynamic Absorber Using Electromagnet | |
| CN112982704B (en) | Series-parallel tuned inerter damper | |
| KR20030050623A (en) | variable inertia type torsional vibration damper | |
| CN113906237B (en) | Pulse vibration damper for tall, slender buildings and equipment | |
| CN206682184U (en) | A kind of integral shock-absorbing clutch driven plate | |
| Lu et al. | Recent Research on Magnetic Machinery |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20220223 Address after: Tokyo, Japan Patentee after: Shengang Compressor Co.,Ltd. Address before: Japan Hyogo Prefecture Patentee before: Kobe Steel, Ltd. |