CN203867898U - Screw compressor - Google Patents
Screw compressor Download PDFInfo
- Publication number
- CN203867898U CN203867898U CN201420323103.7U CN201420323103U CN203867898U CN 203867898 U CN203867898 U CN 203867898U CN 201420323103 U CN201420323103 U CN 201420323103U CN 203867898 U CN203867898 U CN 203867898U
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- Prior art keywords
- lock
- driving
- pressing chamber
- helical
- driving side
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Links
- 238000005452 bending Methods 0.000 claims abstract description 5
- 238000003825 pressing Methods 0.000 claims description 47
- ZZUFCTLCJUWOSV-UHFFFAOYSA-N furosemide Chemical compound C1=C(Cl)C(S(=O)(=O)N)=CC(C(O)=O)=C1NCC1=CC=CO1 ZZUFCTLCJUWOSV-UHFFFAOYSA-N 0.000 claims description 3
- 238000007789 sealing Methods 0.000 abstract description 6
- 238000005057 refrigeration Methods 0.000 description 10
- 239000003795 chemical substances by application Substances 0.000 description 8
- 239000003507 refrigerant Substances 0.000 description 8
- 230000006835 compression Effects 0.000 description 7
- 238000007906 compression Methods 0.000 description 7
- 230000001276 controlling effect Effects 0.000 description 5
- 239000007921 spray Substances 0.000 description 3
- 239000002184 metal Substances 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 239000012190 activator Substances 0.000 description 1
- 230000001154 acute effect Effects 0.000 description 1
- 238000005520 cutting process Methods 0.000 description 1
- 230000003467 diminishing effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 239000011347 resin Substances 0.000 description 1
- 229920005989 resin Polymers 0.000 description 1
- 238000005507 spraying Methods 0.000 description 1
- 230000008093 supporting effect Effects 0.000 description 1
- 239000006200 vaporizer Substances 0.000 description 1
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- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Disclosed is a screw compressor. The fatigue damage of a gate rotor (50) due to the reverse rotation when a screw rotor (40) is stopped is inhibited in the screw compressor in which positions of the driving force which is applied to the lateral sides (51a, 51b) of a gate (51) from the wall surfaces (41a, 41b) of a spiral groove (41) are changed into sealing points (P1, P2). A bending surface (52) is arranged on the lateral side (51a) of the driving side of the gate (51) and the bending surface (52) and the wall surface (41a) of the spiral groove (41) form the sealing point (P1) of the driving side. A bent surface (53) is formed on the lateral side (51b) of the side which is opposite to the driving side of the gate (51) and the bent surface (53) and the wall surface (41b) of the spiral groove (41) form the sealing point (P2) of the side which is opposite to the driving side.
Description
Technical field
The utility model relates to a kind of helical-lobe compressor, particularly the structure of the lock on the gate rotor of the engagement of the spiral chute on a kind of screw rotor.
Background technique
Up to the present, the helical-lobe compressor using as the compressor of refrigeration air-conditioner etc. has been known to everybody.For example, in patent documentation 1, disclosed helical-lobe compressor is included in the discoid gate rotor that has the screw rotor of a plurality of spiral chutes (teeth groove) on outer circumferential face and have a plurality of locks (tooth).The axle center quadrature of the axle center of gate rotor and screw rotor.By the spiral chute on screw rotor and the lock on gate rotor, form pressing chamber.
In this helical-lobe compressor, repeat following action, the lock on gate rotor is accompanied by the rotation of screw rotor and moves with respect to the spiral chute on screw rotor, and the volume of pressing chamber dwindles again after expanding.In the time increasing at the capacity of compressor, refrigeration agent is inhaled into pressing chamber, and the volume of pressing chamber dwindles at the beginning, and the refrigeration agent being inhaled into just starts compressed.When pressing chamber is spiral chute while being communicated with ejiction opening, compressed high-pressure refrigerant just sprays from pressing chamber.
As shown in Figure 7, in the disclosed helical-lobe compressor of patent documentation 1, lock 111 on gate rotor 110 and 101 engagements of the spiral chute of screw rotor 100, the edge of pressing chamber 120 1 sides on the bi-side 112,113 of this lock 111 is formed by flexure plane (circular-arc face) 114,115.
Patent documentation 1: Japanese Laid-Open Patent Publication examined patent publication 57-55881 communique
-technical problem that model utility will solve-
Because the inclination of that a part of spiral chute 101 contacting with gate rotor 110 of screw rotor 100 is accompanied by rotation and changes to B from the A shown in Fig. 7, so be flexure plane 114,115 in the situation that make the edge on the side 112,113 of gate rotor 110, the position that load acts on seal point P1, P2 (point that spiral fluted wall contacts with the side essence of lock) on lock 111 changes.
Gate rotor 110 run well be rotated in the forward time (following with the left surface in Fig. 7, the face that is called driving side) contact with the spiral chute 101 on screw rotor 100, the bight C1 that is positioned at pressing chamber 120 1 sides on lock 111 becomes obtuse angle with respect to this contact position (seal point P1).Because C1Wei obtuse angle, this bight, so even by allowing the edge of driving side side 112 of lock 111 be flexure plane 114, the change in location of seal point P1 and approach described bight C1 can not produce excessive stress on gate rotor 110 yet.
On the other hand, helical-lobe compressor generally sprays high-pressure refrigerant (low voltage side) reverse flow towards suction side of side when stopping, screw rotor 100 counter-rotatings, so when this counter-rotating, lock on gate rotor 110 111 can with screw rotor 100 on the right flank of spiral chute 101 in Fig. 7 (following, the face that is called driving side opposition side) contact, this contact position becomes seal point P2.Because the bight C2 that is positioned at pressing chamber 120 sides of lock 111 becomes acute angle with respect to the seal point P2 of this driving side opposition side, so when the change in location of sealing point P2 and while approaching described bight C2, will produce excessive stress on gate rotor 110.And, if repeat start and stop under the larger condition of height pressure reduction, just likely cause the bight C2 fatigue damage that is positioned at driving side opposition side of gate rotor 110.
Model utility content
The utility model is just for having addressed the above problem.Its object is: suppress gate rotor due to the counter-rotating of screw rotor when stopping fatigue damage.
-model utility for the technological scheme of technical solution problem-
The following helical-lobe compressor of model utility of first aspect is prerequisite, a kind of helical-lobe compressor, it is included in the screw rotor 40 on outer circumferential face with a plurality of spiral chutes 41 and the discoid gate rotor 50 with a plurality of locks 51, and the plurality of lock 51 forms pressing chamber 23 with these spiral chute 41 engagements.Described lock 51 has driving side side 51a and driving side opposition side side 51b.This driving side side 51a is when described screw rotor 40 is rotated in the forward, wall 41a by described spiral chute 41 drives, this driving side opposition side side 51b is positioned at a contrary side of described driving side side 51a, this driving side opposition side side 51b is when described screw rotor 40 counter-rotating, wall 41b by described spiral chute 41 drives, and the point of action that acts on the driving force of side 51a, 51b described lock 51 from wall 41a, the 41b of described spiral chute 41 becomes seal point P1, P2.
In this helical-lobe compressor, the driving side side 51a of described lock 51 has flexure plane 52 in the edge of described pressing chamber 23 sides, by the curved part of this flexure plane 52 and the wall 41a of described spiral chute 41, forms described seal point P1; The driving side opposition side side 51b of described lock 51 has folding surface 53 in the edge of described pressing chamber 23 sides, by the bending part of this folding surface 53 and the wall 41b of described spiral chute 41, forms described seal point P2.
In the model utility of this first aspect, at the driving side of lock 51, because being forms seal point P1 by the spiral chute 41 on flexure plane 52 and screw rotor 40, so can suppress lock 51 wearing and tearing; At the driving side opposition side of lock 51, because being forms seal point P2 by the spiral chute 41 on folding surface 53 and screw rotor 40, so the position of seal point P2 is necessarily constant.
The model utility of second aspect is such, and in the model utility of first aspect, this helical-lobe compressor comprises: the driving mechanism 15 of screw rotor 40 described in variable speed drives.
In the model utility of this second aspect, in the situation that be the helical-lobe compressor of variable speed drives, because guiding valve is not to use as unloading mechanism, but use as volume ratio controlling mechanism, so cannot off-load during counter-rotating, the load that imposes on gate rotor 50 is just excessive.With respect to this, can effectively suppress this load and cause producing stress.
The model utility of the third aspect is such, first or the model utility of second aspect in, the seal point P2 of the driving side opposition side of described lock 51 is formed on from the bight C2 of pressing chamber 23 sides of described lock 51 and counts in the scope of distance below the above 1.2mm of 0.8mm.
The model utility of fourth aspect is such, and in the model utility of the third aspect, the seal point P2 of the driving side opposition side of described lock 51 is formed on and counts distance from the bight C2 of pressing chamber 23 sides of described lock 51 is the position of 1.0mm.
In the model utility of above-mentioned the 3rd, fourth aspect, the seal point P2 of the driving side opposition side of lock 51 can be set on position very suitable for the bight C2 of compressing surface side.
The model utility of the 5th aspect is such, first or the model utility of second aspect in, the seal point P1 of the driving side of described lock 51 is formed on from the bight C1 of pressing chamber 23 sides of described lock 51 and counts in the scope of distance below the above 1.6mm of 0.3mm.
The model utility of the 6th aspect is such, and in the model utility of the third aspect, the seal point P1 of the driving side of described lock 51 is formed on from the bight C1 of pressing chamber 23 sides of described lock 51 and counts in the scope of distance below the above 1.6mm of 0.3mm.
The model utility of the 7th aspect is such, and in the model utility of fourth aspect, the seal point P1 of the driving side of described lock 51 is formed on from the bight C1 of pressing chamber 23 sides of described lock 51 and counts in the scope of distance below the above 1.6mm of 0.3mm.
Aspect the above-mentioned the 5th, in the model utility of either side in the 7th aspect, the seal point P1 of the driving side of lock 51 can be set on position very suitable for the bight C1 of pressing chamber 23 sides.
-effect of model utility-
According to the utility model, at the driving side opposition side of lock 51, by the spiral chute 41 on folding surface 53 and screw rotor 40, form seal point P2, the position of seal point P2 is necessarily constant, therefore there will not be seal point P2 from the bight C2 of lock 51 situation close to excessively.Therefore, can prevent from lock 51, producing excessive stress, thereby can suppress lock 51 fatigue damages.
According to the model utility of above-mentioned second aspect, in the easy excessive variable speed drives helical-lobe compressor of the load that imposes on gate rotor 50, can effectively suppress when screw rotor 40 counter-rotating time gating 51 fatigue damages.
According to the above-mentioned the 3rd or the model utility of fourth aspect because seal point P2 not can from the bight C2 that is positioned at pressing chamber 23 sides of lock 51 excessively close to, so can effectively suppress the stress of lock 51, increase; And because seal point P2 also not can from this bight C2 excessively away from, so can effectively suppress leakage loss.
According to the model utility of either side in above-mentioned the 5th to the 7th aspect, cause is by flexure plane 52, to be formed the seal point P1 of the driving side of lock 51, so gate rotor 50 wearing and tearing in the time of can suppressing to run well, and, by seal point P1 is set in described scope, can realize that leakage loss is few, the running of excellent in efficiency.
Accompanying drawing explanation
Fig. 1 is the structural section map that the first working state of the related helical-lobe compressor of mode of execution of the present utility model is shown.
Fig. 2 is the structural section map that the second working state of the helical-lobe compressor in Fig. 1 is shown.
Fig. 3 is the sectional view of cutting open along the A-A line in Fig. 1.
Fig. 4 is the stereogram that the engagement of screw rotor and gate rotor is shown.
Fig. 5 (A)～Fig. 5 (C) is the plan view that the working condition of compressing mechanism is shown, and Fig. 5 (A) represents suction stroke, and Fig. 5 (B) represents compression stroke, and Fig. 5 (C) represents ejection stroke.
Fig. 6 is illustrated in the section shape that is positioned at this locational that a part of lock of engaging piece of screw rotor and gate rotor in the helical-lobe compressor of present embodiment.
Fig. 7 is illustrated in the section shape of this locational that a part of lock of engaging piece in screw rotor and gate rotor in the helical-lobe compressor of prior art.
-symbol description-
1-helical-lobe compressor; 15-driving mechanism; 23-pressing chamber; 40-screw rotor; 41-spiral chute; 41a-wall; 41b-wall; 50-gate rotor; 51-lock; 51a-driving side side; 51b-driving side opposition side side; 52-flexure plane; 53-folding surface; C1-bight; C2-bight; P1-seal point; P2-seal point.
Embodiment
Below, with reference to accompanying drawing, mode of execution of the present utility model is described in detail.
The helical-lobe compressor 1 of present embodiment is arranged in the refrigerant circuit that carries out refrigeration cycle, for refrigeration agent is compressed.
As shown in Figure 1, in helical-lobe compressor 1, compressing mechanism 20 and its motor 15 of driving are arranged in a casing 30.Casing 30 inside are formed with a distolateral low-voltage space S1 who is positioned at casing 30 and another the distolateral high-pressure space S2 that is positioned at casing 30.Refrigeration agent is introduced low-voltage space S1 by the vaporizer from refrigerant circuit, and refrigeration agent is fed to the condenser refrigerant circuit from high-pressure space S2.
Motor 15 is arranged in the low-voltage space S1 of casing 30 inside, and compressing mechanism 20 is arranged between low-voltage space S1 and high-pressure space S2.The live axle 21 of compressing mechanism 20 connects with motor 15.Though not shown, this motor 15 is connected with frequency variator, form the driving mechanism of variable speed drives aftermentioned screw rotor 40.
Helical-lobe compressor 1 comprises the motor 15 of compressing mechanism 20, drive compression mechanism 20 and for regulating the volume ratio controlling mechanism 3 of the internal capacity ratio of compressing mechanism 20.
As shown in FIG. 1 to 3, compressing mechanism 20 comprise the cylinder part 31 that is formed in casing 30, be arranged in cylinder part 31 and screw rotor 40 that can rotate and with two gate rotors 50 of screw rotor 40 engagements.
In circumferential two positions of cylinder part 31, be formed with valve folding and unfolding portion 32 (with reference to Fig. 4).Valve folding and unfolding portion 32 bloats towards the radial outside of cylinder part 31.This valve folding and unfolding portion 32 comprises the axially extended chute 33 along cylinder part 31.Guiding valve 4 described later is arranged in chute 33, can be along axially moving in chute 33.
Screw rotor 40 connects through live axle 21 and motor 15.Live axle 21 is arranged to screw rotor 40 coaxial.The tip portion of live axle 21 is supported by ball bearing 61.Ball bearing 61 is arranged on bearing support 60.
As Figure 1 and Figure 4, screw rotor 40 is cylindrical metal member mades roughly.On the outer circumferential face of screw rotor 40, be formed with a plurality of (being in the present embodiment 6) spiral chute 41, this spiral chute 41 from one end (end, suction side) of screw rotor 40 towards the other end (ejection side end) spiral extension.
Each gate rotor 50 is resin parts.As shown in Figure 4, the tabular lock 51 of a plurality of (being in the present embodiment 11) rectangular is arranged on each gate rotor 50 radially.Each gate rotor 50 is arranged in cylinder part 31 outsides axisymmetricly with respect to the running shaft of screw rotor 40 state.Each gate rotor 50 is arranged to spiral chute 41 engagements on a part (not shown) that lock 51 on it runs through cylinder part 31 and screw rotor 40.
Gate rotor 50 is arranged on metal rotor bearing parts 55 processed (with reference to Fig. 4).The rotor bearing parts 55 that gate rotor 50 is installed are arranged on adjacent with cylinder part 31 and in casing 30, are spaced and in the gate rotor chamber 90 that forms (with reference to Fig. 3).The axial region 58 of each rotor bearing parts 55, rotates freely by the bearing fixed block in gate rotor chamber 90 (bearing housing) 91 supportings through ball bearing 92,93.In addition, each gate rotor chamber 90 is communicated with low-voltage space S1.
In compressing mechanism 20, the space being surrounded by the inner peripheral surface of cylinder part 31, spiral chute 41 on screw rotor 40 and the lock 51 on gate rotor 50 becomes pressing chamber 23.
As mentioned above, helical-lobe compressor 1 comprises for regulating the internal capacity of compressing mechanism 20 than the volume ratio controlling mechanism 3 of Vi.This internal capacity than Vi refer to the zero hour of compression stroke pressing chamber 23 volume V 1 with in compression stroke the finish time pressing chamber 23 volume V 2 ratio (V1/V2).
Described volume ratio controlling mechanism 3 has above-mentioned chute 33 and guiding valve 4, in order to change the valve modified gear 18 of the position of guiding valve 4 in chute 33.
Guiding valve 4 comprises main body portion 4a and guide portion 4b.Main body portion 4a is column.Main body portion 4a above with screw rotor 40 sliding contacts, towards pressing chamber 23; Its back side and casing 30 sliding contacts.Guide portion 4b is and crooked thick plate-like outstanding from the cardinal extremity of main body portion 4a (right-hand member Fig. 2, Fig. 3).The back side of guide portion 4b and casing 30 sliding contacts.
As mentioned above, in cylinder part 31, be formed with two chutes 33.Each chute 33 is arranged respectively to a guiding valve 4.In cylinder part 31, the part that to take from the cardinal extremity of the main body portion 4a of guiding valve 4 be benchmark high-pressure space S2 side becomes the ejiction opening that allows pressing chamber 23 be communicated with high-pressure space S2.
Guiding valve 4, in chute 33 from primary importance (position shown in Fig. 2) farthest of the ejection side end of screw rotor 40 (near the end of high-pressure space S2) with freely slide along the parallel direction of rotary middle spindle essence with screw rotor 40 between the nearest second place of this ejection side end (position shown in Fig. 1).
Valve activator 18 comprises driving with cylinder 6 and is arranged on the piston 7 in cylinder 6 for this driving.And piston 7 is connected through arm 9 and connecting rod 10 and two guiding valves 4.When piston 7 moves, each guiding valve 4 will move towards the direction identical with piston 7 distance identical with piston 7.If guiding valve 4 moves, before being soon communicated with ejiction opening 25, the volume of (that is, compression stroke the finish time) pressing chamber 23 will change, so the internal capacity of compressing mechanism 20 can change than Vi.
Next, the structure of the lock 51 of gate rotor 50 is explained.In Fig. 6, lock 51 have when screw rotor 40 is rotated in the forward driving side side 51a (side in left side in Fig. 6) that the wall 41a by spiral chute 41 drives and, be arranged in a contrary side of this driving side side 51a and when screw rotor 40 counter-rotating by the driving side opposition side side 51b (side on Fig. 6 right side) of the wall 41b driving of spiral chute 41.The point of action of driving force that acts on side 51a, the 51b of described lock 51 from wall 41a, the 41b of spiral chute 41 becomes seal point P1, P2.
In present embodiment, the driving side side 51a of lock 51 has flexure plane 52 in the edge of pressing chamber 23 sides, by the curved part of this flexure plane 52 and the wall 41a of described spiral chute 41, forms described seal point P1.The inclination of spiral chute 41 is accompanied by screw rotor 40 rotations and changes to B from A, and the inclination that the position of sealing point P1 is accompanied by spiral chute 41 changes to B and changes from A.The driving side opposition side side 51b of lock 51 has folding surface 53 in the edge of pressing chamber 23 sides, by the bending part of this folding surface 53 and the wall 41b of described spiral chute 41, forms described seal point P2.Even if the angle of spiral chute 41 is accompanied by screw rotor 40 rotations and changes, the position of sealing point P2 can not change yet.
The seal point P2 of the driving side opposition side of described lock 51 is formed on from the bight C2 that is positioned at driving side opposition side and pressing chamber 23 sides of this lock 51 and counts the position of distance for 1.0mm.The bight C1 that is positioned at driving side and pressing chamber 23 sides that the seal point P1 of the driving side of described lock 51 is formed on from lock 51 is counted the scope below the above 1.6mm of 0.3mm.
-working condition of helical-lobe compressor-
With reference to Fig. 5 (A)～Fig. 5 (C), illustrate how helical-lobe compressor 1 sucks and refrigeration agent is compressed.
In the compressing mechanism 20 of in running order helical-lobe compressor 1, carry out spraying stroke shown in compression stroke shown in suction stroke shown in Fig. 5 (A), Fig. 5 (B) and Fig. 5 (C).During suction stroke that this helical-lobe compressor expands at the volume that carries out pressing chamber 23, the low-pressure gaseous refrigerant in low-voltage space S1 is inhaled into pressing chamber 23.When carrying out the diminishing compression stroke of volume of pressing chamber 23, gaseous refrigerant in pressing chamber 23 is compressed, when becoming the ejection stroke that pressing chamber 23 is communicated with high-pressure space S2 through ejiction opening 25, compressed high-pressure gaseous refrigerant just sprays to high-pressure space S2 from pressing chamber 23 by ejiction opening 25.
Here, in the helical-lobe compressor 1 of present embodiment, make the shape of the lock 51 on gate rotor 50 as described below, flexure plane 52 is located to driving side and forms seal point P1 by the wall 41a of the spiral chute 41 on this flexure plane 52 and screw rotor 40, folding surface 53 is located to driving side opposition side and forms seal point P2 by the wall 41b of the spiral chute 41 on this folding surface 53 and screw rotor 40.
At driving side, by form seal point P1 on flexure plane 52, just can reduce the leakage of refrigeration agent.On the other hand, at driving side opposition side, by form seal point P2 on folding surface 53, the position of seal point P2 just can not change, thus can not occur seal point P2 from the bight C2 that is positioned at pressing chamber 23 sides of the driving side opposition side side 51b of lock 51, cross close to such situation.
-effect of mode of execution-
According to present embodiment, because being is formed the seal point P2 of the driving side opposition side of lock 51 by folding surface 53, make the position of seal point P2 necessarily constant, so can suppress to produce excessive stress at the bight of gate rotor 50 C2 when screw rotor 40 counter-rotating.Therefore can prevent gate rotor 50 fatigue damages.If the seal point P2 of the driving side opposition side on lock 51 from the bight C2 that is positioned at driving side opposition side and pressing chamber 23 sides of this lock 51 excessively away from, leakage loss can increase.With respect to this, in the present embodiment, because allow described seal point P2 be formed on from described bight C2, count the position of distance for 1.0mm, so can suppress leakage loss, increase.
In the situation that using volume ratio controlling mechanism 3, speed change helical-lobe compressor 1 cannot off-load when counter-rotating, so counter-rotating meeting aggravation, the load being added in during counter-rotating on gate rotor 50 increases, and just easily produces fatigue damage.With respect to this, in the present embodiment, can effectively suppress its fatigue damage.
Because the seal point P1 of the driving side of lock 51 is formed by flexure plane, so gate rotor 50 wearing and tearing in the time of can suppressing to run well.Therefore can the good running of implementation efficiency.
By formed the driving side opposition side side 51b of lock 51 by folding surface 53, be easy to processing.From manufacture view, simpler than allowing two side 51a, 51b all become flexure plane; With allow both sides all become flexure plane 52 to compare, while allowing the side of lock 51 1 sides become folding surface 53, more easily to and screw rotor 40 on spiral chute 41 between gap set, the leakage of refrigeration agent reduces and can bring efficiency better to turn round.
(other mode of execution)
Can also adopt in the above-described embodiment following structure.
In the above-described embodiment, allow the seal point P2 of driving side opposition side of lock 51 be formed on from the bight C2 that is positioned at driving side opposition side and pressing chamber 23 sides of lock 51 and count the position that distance is 1.0mm, but can also allow the seal point P2 of driving side opposition side of lock 51 be formed on the position in the scope below the above 1.2mm of 0.8mm.
In addition, above-mentioned mode of execution is preferred example in essence, the intention the utility model, application of the present utility model or purposes scope of the present utility model not being limited.
-industrial applicability-
In sum, the utility model for screw rotor on the gate rotor of spiral chute engagement on lock structure of great use.
Claims (7)
1. a helical-lobe compressor, it is included in the screw rotor (40) on outer circumferential face with a plurality of spiral chutes (41) and the discoid gate rotor (50) with a plurality of locks (51), the plurality of lock (51) forms pressing chamber (23) with this spiral chute (41) engagement
Described lock (51) has driving side side (51a) and driving side opposition side side (51b),
This driving side side (51a), when described screw rotor (40) is rotated in the forward, is driven by the wall (41a) of described spiral chute (41),
This driving side opposition side side (51b) is positioned at a contrary side of described driving side side (51a), this driving side opposition side side (51b) is when described screw rotor (40) counter-rotating, wall (41b) by described spiral chute (41) drives
The point of action that acts on the driving force of the side (51a, 51b) described lock (51) from the wall (41a, 41b) of described spiral chute (41) becomes seal point (P1, P2), it is characterized in that:
The driving side side (51a) of described lock (51) has flexure plane (52) in the edge of described pressing chamber (23) side, by the curved part of this flexure plane (52) and the wall of described spiral chute (41), (41a forms described seal point (P1)
The driving side opposition side side (51b) of described lock (51) has folding surface (53) in the edge of described pressing chamber (23) side, by the bending part of this folding surface (53) and the wall (41b) of described spiral chute (41), forms described seal point (P2).
2. helical-lobe compressor according to claim 1, is characterized in that:
This helical-lobe compressor comprises: the driving mechanism (15) of screw rotor described in variable speed drives (40).
3. helical-lobe compressor according to claim 1 and 2, is characterized in that:
The seal point (P2) of the driving side opposition side of described lock (51) is formed on from the bight (C2) of pressing chamber (23) side of described lock (51) and counts in the scope below the above 1.2mm of 0.8mm.
4. helical-lobe compressor according to claim 3, is characterized in that:
The seal point (P2) of the driving side opposition side of described lock (51) is formed on from the bight (C2) of pressing chamber (23) side of described lock (51) and counts the position of distance for 1.0mm.
5. helical-lobe compressor according to claim 1 and 2, is characterized in that:
The seal point (P1) of the driving side of described lock (51) is formed on from the bight (C1) of pressing chamber (23) side of described lock (51) and counts in the scope of distance below the above 1.6mm of 0.3mm.
6. helical-lobe compressor according to claim 3, is characterized in that:
The seal point (P1) of the driving side of described lock (51) is formed on from the bight (C1) of pressing chamber (23) side of described lock (51) and counts in the scope of distance below the above 1.6mm of 0.3mm.
7. helical-lobe compressor according to claim 4, is characterized in that:
The seal point (P1) of the driving side of described lock (51) is formed on from the bight (C1) of pressing chamber (23) side of described lock (51) and counts in the scope of distance below the above 1.6mm of 0.3mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420323103.7U CN203867898U (en) | 2014-06-17 | 2014-06-17 | Screw compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420323103.7U CN203867898U (en) | 2014-06-17 | 2014-06-17 | Screw compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203867898U true CN203867898U (en) | 2014-10-08 |
Family
ID=51648858
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420323103.7U Expired - Lifetime CN203867898U (en) | 2014-06-17 | 2014-06-17 | Screw compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203867898U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109312743A (en) * | 2016-06-14 | 2019-02-05 | 大金工业株式会社 | Helical-lobe compressor |
-
2014
- 2014-06-17 CN CN201420323103.7U patent/CN203867898U/en not_active Expired - Lifetime
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109312743A (en) * | 2016-06-14 | 2019-02-05 | 大金工业株式会社 | Helical-lobe compressor |
| CN109312743B (en) * | 2016-06-14 | 2019-12-27 | 大金工业株式会社 | Screw compressor |
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Granted publication date: 20141008 |