CN101918716A - Gate rotor and screw compressor - Google Patents
Gate rotor and screw compressor Download PDFInfo
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- CN101918716A CN101918716A CN2008801228982A CN200880122898A CN101918716A CN 101918716 A CN101918716 A CN 101918716A CN 2008801228982 A CN2008801228982 A CN 2008801228982A CN 200880122898 A CN200880122898 A CN 200880122898A CN 101918716 A CN101918716 A CN 101918716A
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- gate rotor
- rotor
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- screw
- gate
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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
- F04C18/48—Rotary-piston pumps with non-parallel axes of movement of co-operating members
- F04C18/50—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees
- F04C18/52—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
- F01C17/02—Arrangements for drive of co-operating members, e.g. for rotary piston and casing of toothed-gearing 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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
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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
- F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
- F04C27/001—Radial sealings for working fluid
- F04C27/004—Radial sealing elements specially adapted for intermeshing-engagement type pumps, e.g. gear pumps
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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
- F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
- F04C29/0078—Fixing rotors on shafts, e.g. by clamping together hub and shaft
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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
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
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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
- F04C2240/00—Components
- F04C2240/50—Bearings
- F04C2240/52—Bearings for assemblies with supports on both sides
-
- 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
- F04C2240/60—Shafts
- F04C2240/603—Shafts with internal channels for fluid distribution, e.g. hollow shaft
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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
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/16—Wear
-
- 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
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/17—Tolerance; Play; Gap
-
- 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
- F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
- F04C27/007—Sealings for working fluid between radially and axially moving parts
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
A screw compressor which can prevent capacity decrease by a simple arrangement, even when a gate rotor bends during operation due to a temperature difference between a casing and a screw rotor, by preventing the gate rotor from biting into the screw rotor, thereby reducing abrasion of the gate rotor. A gate rotor (3) has a gate rotor main body (30), and a shaft portion (40) for fixing the gate rotor main body (30). A resilient body (5) is arranged in a space (S) between a shaft (41) of the shaft portion (40) and a hole (32) of the gate rotor body (30).
Description
Technical field
The screw compressor that this invention relates to gate rotor and uses this gate rotor.
Background technique
In the prior art, as screw compressor, shown in the enlarged cross section figure of Figure 16, in the cylinder body 210 of housing 201, take in screw rotor 202, this screw rotor 202 and gate rotor 203 engagements by the pressing chamber that is meshing with each other and forms of above-mentioned screw rotor 202 and above-mentioned gate rotor 203, are used for pressurized gas (with reference to No. 3731399 communique of Japan Patent: patent documentation 1).
That is, the slot part 221 of above-mentioned screw rotor 202 and 231 engagements of the tooth portion of above-mentioned gate rotor 203 form above-mentioned pressing chamber.To above-mentioned compressor, distolateral from the axle 202a direction of above-mentioned screw rotor 202 sucks the gas of low pressure, compresses this low-pressure gas at above-mentioned pressing chamber, with another the distolateral ejection from the axle 202a direction of above-mentioned screw rotor 202 of these compressed pressurized gas.
Above-mentioned gate rotor 203 comprises: have the gate rotor main body 230 of above-mentioned tooth portion 231 and fix the axial region 240 of this gate rotor main body 230.Above-mentioned axial region 240 is supported on the above-mentioned housing 201.
At this, in the running of compressor, by above-mentioned pressing chamber pressurized gas, above-mentioned screw rotor 202 is a high temperature, and it is big that the thermal expansion of above-mentioned screw rotor 202 becomes.On the other hand, the gate rotor chamber L that takes in above-mentioned gate rotor 203 in the above-mentioned housing 201 is a low pressure, and the gas that is in this gate rotor chamber L is relative low temperature, and therefore, the thermal expansion of above-mentioned gate rotor chamber L peripheral part of above-mentioned housing 201 is little.Part around the gate rotor chamber L of this housing 201 is the part of the distance between the axle 203a of the axle 202a that determines above-mentioned screw rotor 202 and above-mentioned gate rotor 203.
Patent documentation 1: No. 3731399 communique of Japan Patent
But, above-mentioned existing screw compressor, above-mentioned gate rotor 203 is supported on the above-mentioned housing 201, in the running of compressor, the thermal expansion of above-mentioned screw rotor 202 is big, the thermal expansion of above-mentioned on the other hand housing 201 is little, can produce the problem of the variable in distance between the axle 203a of axle 202a and above-mentioned gate rotor 203 of above-mentioned screw rotor 202.That is, in the running of compressor, the temperature difference of above-mentioned housing 201 and above-mentioned screw rotor 202 can be brought the problem of above-mentioned gate rotor 203 bendings.
Therefore at this moment, above-mentioned gate rotor main body 230 is fixed on the above-mentioned axial region 240, and the tooth portion 231 of above-mentioned gate rotor main body 230 invades the slot part 221 of above-mentioned screw rotor 202, and the loss quantitative change of above-mentioned tooth portion 231 is big.
This result, it is big that the slit of the tooth portion 231 of above-mentioned gate rotor main body 230 and the slot part 221 of above-mentioned screw rotor 202 becomes, and the performance of compressor reduces.
In addition, above-mentioned existing screw compressor, part around the above-mentioned cylinder body 210 in the above-mentioned housing 201 is provided with the hyperbaric chamber, the temperature difference of above-mentioned housing 201 and above-mentioned screw rotor 202 diminishes, part around the above-mentioned gate rotor chamber L of above-mentioned housing 201 is not provided with the hyperbaric chamber, can not eliminate the bending of above-mentioned gate rotor 203.
Summary of the invention
At this, problem of the present invention is to provide a kind of compressor, in the running of compressor, even because the temperature difference of housing and screw rotor produces the gate rotor bending, also can prevent gate rotor intrusion screw rotor, reduce the breakage of gate rotor by simple structure, the ability that prevents compressor reduces, the screw rotor that also provides this compressor to use.
In order to solve above-mentioned problem, the gate rotor of first invention, comprise the gate rotor main body and the shaft of this gate rotor main body is installed, described gate rotor main body comprises a plurality of tooth portions and is positioned at the hole portion of central authorities, described shaft comprises platform portion and axial region, described portion be in the described gate rotor main body of its one side upper support, and described axial region is arranged on the described one side of this one and is inserted into described hole portion, disposes elastomer between the hole portion of the axial region of described shaft and described gate rotor main body.
According to the gate rotor of this invention, dispose elastomer between the hole portion of the axial region of above-mentioned shaft and above-mentioned gate rotor main body, therefore above-mentioned gate rotor main body can be slided in above-mentioned portion of above-mentioned shaft.
Therefore, in screw compressor, use this gate rotor, the tooth portion of above-mentioned gate rotor main body and screw rotor engagement, and above-mentioned shaft is supported under the situation on the housing, in the running of compressor, the thermal expansion of above-mentioned screw rotor is big, on the other hand, the thermal expansion of above-mentioned housing is little, even the axle of the axle of above-mentioned screw rotor and above-mentioned gate rotor (promptly, the axial region of above-mentioned shaft) variable in distance between, above-mentioned gate rotor main body is slided in above-mentioned portion of above-mentioned shaft, and the position relation of above-mentioned screw rotor and above-mentioned gate rotor main body is kept suitable distance.
This result can prevent that above-mentioned gate rotor main body from invading above-mentioned screw rotor, reduces the breakage of above-mentioned gate rotor main body, prevents that the ability of compressor from reducing.In addition, can reduce above-mentioned gate rotor main body and above-mentioned screw rotor and push the invalid power that brings mutually.In addition, by above-mentioned elastomer, the crimp force of above-mentioned gate rotor main body and above-mentioned screw rotor can be remained on the degree that gas does not leak.
Therefore, in the running of compressor,, also can prevent gate rotor intrusion screw rotor, reduce the breakage of gate rotor, prevent that the ability of compressor from reducing by simple structure even because the temperature difference of housing and screw rotor produces the bending of gate rotor.
In addition, the gate rotor of second invention, above-mentioned elastomer is a leaf spring.
According to the gate rotor of second invention, above-mentioned elastomer is a leaf spring, and above-mentioned elastomer can simply constitute.
In addition, the gate rotor of the 3rd invention, above-mentioned leaf spring is the wavy spring or the spiral spring of ring-type.
According to the gate rotor of the 3rd invention, above-mentioned leaf spring is the wavy spring or the spiral spring of ring-type, can simply constitute above-mentioned leaf spring.
In addition, the gate rotor of the 4th invention, above-mentioned elastomer is the rubber of ring-type.
According to the gate rotor of the 4th invention, above-mentioned elastomer is the rubber of ring-type, can simply constitute elastomer.
In addition, the screw compressor of the 5th invention is characterised in that, comprising: the housing with cylinder body; The cylindraceous screw rotor chimeric with this cylinder body; With with the above-mentioned gate rotor of this screw rotor engagement, the tooth portion of the described gate rotor main body of described gate rotor meshes with described screw rotor, the described shaft of described gate rotor is by described housings support.
Screw compressor according to the 5th invention, comprise above-mentioned gate rotor, therefore in the running of compressor, it is big that the thermal expansion of above-mentioned screw rotor becomes, on the other hand, the thermal expansion of above-mentioned housing diminishes, even variable in distance between the axle of above-mentioned screw rotor and the axle (that is, the axle of above-mentioned shaft) of above-mentioned gate rotor is like this, above-mentioned gate rotor main body is slided in above-mentioned portion of above-mentioned shaft, and the position relation of above-mentioned screw rotor and above-mentioned gate rotor main body also can be kept suitable distance.
This result can prevent that above-mentioned gate rotor main body from invading above-mentioned screw rotor, reduces the breakage of above-mentioned gate rotor main body, prevents that the ability of compressor from reducing.In addition, reduce above-mentioned gate rotor main body and the mutual brute force of above-mentioned screw rotor is pushed the useless power that brings.In addition, utilize above-mentioned elastomer, the crimp force of above-mentioned gate rotor main body and above-mentioned screw rotor can be remained on gastight degree.
Therefore, in the running of compressor,, also can prevent gate rotor intrusion screw rotor, reduce the breakage of gate rotor, prevent that the ability of compressor from reducing by simple structure even because the temperature difference of housing and screw rotor produces the bending of gate rotor.
The screw compressor of the 6th invention comprises: screw rotor, gate rotor, gate rotor rotating shaft, elastomer.Screw rotor has a plurality of spiral helicine grooves and can rotate freely at outer circumferential face.Gate rotor is formed with opening in central authorities.Around the opening of gate rotor, dispose the tooth of the groove engagement of a plurality of and screw rotor radially.The gate rotor rotating shaft is inserted into the opening of gate rotor with the state with slit.Elastomer is configured in the opening and the slit between the gate rotor rotating shaft of gate rotor, and/or be configured in be used for stopping gate rotor around a plurality of spline pins of the rotation of gate rotor rotating shaft at least one around.
Screw compressor according to the 6th invention, around the gate rotor rotating shaft, form the slit, elastomer is configured in the slit on every side of gate rotor rotating shaft, and/or be configured in stop in a plurality of spline pins of the rotation of gate rotor rotating shaft at least one around, thus, can absorb the elongation of footpath direction of the tooth of gate rotor.
The screw compressor of the 7th invention is the screw compressor of the 6th invention, is configured in the elastomer in slit, with respect to 1 elastic force that apply to the radial direction of gate rotor of gate rotor towards a plurality of spline pins.
According to the screw compressor of the 7th invention, be configured in the elastomer in slit, with respect to gate rotor, towards the spline pin, apply elastic force to the radial direction of gate rotor, thus, the tooth that moves to radial direction that constraint spline pin brings is effectively absorbed by elastomer in the elongation of radial direction.
The screw compressor of the 8th invention is the screw compressor of the 6th invention, and the elastomer that is configured in the slit is a ring-type, this elastomer-filled whole slit.
According to the screw compressor of the 8th invention, be ring-type at the elastomer of slot arrangement, and fill whole slit, thus, can absorb of the elongation of the tooth of gate rotor in the footpath direction.In addition, by the elastomer-filled slit integral body of ring-type, can further prolong the life-span of the tooth of gate rotor.
The screw compressor of the 9th invention is the 6th to invent each screw compressor in the 8th invention, and 1 in a plurality of spline pins is the pin that floats.Float pin (play pin) for being connected between gate rotor rotating shaft and the gate rotor comparing under the state with play with other spline pin.
Screw compressor according to the 9th invention, 1 of a plurality of spline pins, be for comparing state with other spline pin, being connected the unsteady pin between described gate rotor rotating shaft and the described gate rotor with play, thus, unsteady pin can be obtained the mobility bigger than other spline pin, can absorb the elongation of footpath direction of the tooth of gate rotor.
The screw compressor of the tenth invention is the screw compressor of the 9th invention, and elastomer is a ring-type, is configured in as around the unsteady spline pin of selling.
The screw compressor of the tenth invention, elastomer is a ring-type, is configured in as around the spline pin of the pin that floats, and can absorb the elongation of footpath direction of the tooth of gate rotor.
Gate rotor according to first invention, between the hole portion of the axial region of above-mentioned shaft and above-mentioned gate rotor main body, dispose elastomer, thus, use at screw compressor under the situation of this gate rotor, in the running of compressor, even because the temperature difference of housing and screw rotor produces the bending of gate rotor, also can be by simple structure, prevent gate rotor intrusion screw rotor, reduce the breakage of gate rotor, prevent that the ability of compressor from reducing.
According to second invention, elastomer can simply constitute.
According to the 3rd invention, leaf spring can simply constitute.
According to the 4th invention, elastomer can simply constitute.
Screw compressor according to the 5th invention, because possess above-mentioned gate rotor, therefore, in the running of compressor, even because the temperature difference of housing and screw rotor produces the bending of gate rotor, also can prevent gate rotor intrusion screw rotor by simple structure, reduce the breakage of gate rotor, prevent that the ability of compressor from reducing.
According to the 6th invention, can absorb the elongation of footpath direction of the tooth of gate rotor.Thus, the tooth front end of the tooth of gate rotor can not wear and tear at the interior wall friction of the groove of screw rotor, can prevent the loss of gate rotor.
According to the 7th invention, can retrain the tooth that moves to radial direction by the spline pin, can effectively absorb the elongation of radial direction by elastomer.
According to the 8th invention, can absorb the elongation of footpath direction of the tooth of gate rotor, and the elastomer of ring-type buries slit integral body, can further prolong the life-span of the tooth of gate rotor.
According to the 9th invention, unsteady pin can be obtained the mobility bigger than other spline pin, can absorb the elongation of footpath direction of the tooth of gate rotor.
According to the tenth invention, can absorb the elongation of footpath direction of the tooth of gate rotor.
Description of drawings
Fig. 1 is the cross-sectional view of first mode of execution of expression gate rotor of the present invention and screw compressor.
Fig. 2 is the plan view of the gate rotor main body of Fig. 1.
Fig. 3 is the A-A sectional view of Fig. 2.
Fig. 4 is the plan view of the shaft of Fig. 1.
Fig. 5 is the B-B sectional view of Fig. 4.
Fig. 6 is the plan view of the gate rotor of Fig. 1.
Fig. 7 is the C-C sectional view of Fig. 6.
Fig. 8 is the planimetric map of second mode of execution of expression gate rotor of the present invention.
Fig. 9 is the structural drawing of major component of the single-screw compressor of the 3rd mode of execution of the present invention.
Figure 10 is the front elevation of the single-screw compressor of Fig. 9.
Figure 11 is the structural drawing of the configuration of the screw rotor of presentation graphs 9 and gate rotor.
Figure 12 is the gate rotor of Fig. 9 and the engaging portion that gate rotor supports, and (a) is front elevation, (b) is back elevation.
Figure 13 be Fig. 9 the gate rotor rotating shaft around the expanded view of coil spring peripheral part of slot arrangement.
Figure 14 is the breach front elevation of gate rotor, gate rotor support and the gate rotor rotating shaft of Fig. 9.
Hole and O shape ring part enlarged cross section figure on every side that Figure 15 uses for the rotation condition of the gate rotor of Figure 11.
Figure 16 is the enlarged cross section figure of existing screw compressor.
Symbol description
1 housing
10 cylinder bodies
11 sealing surfaces
12 through holes
13 ejiction openings
2 screw rotors
The 2a axle
21 slot parts
3,3A gate rotor
The 3a axle
30 gate rotor main bodys
The 30a axle
31 tooth portions
32 hole portions
33 pin-and-holes
40 shafts
The 40a axle
41 the first axle parts
42 the second axle parts
43 portions
The 43a one side
44 tooth portions
45 pin-and-holes
5 elastomers (leaf spring)
5A elastomer (rubber)
The C pressing chamber
L gate rotor chamber
S slit (gap) 101 screw compressors
102 screw rotors
103 shells
104 rotating shafts
105 first gate rotors
106 second gate rotors
108,109 gate rotor rotating shafts
111 grooves
112 teeth
121 openings
122 slits (gap)
123 guide finger
124 float sells (play pin)
127 gate rotors support
128 coil springs (first elastomer)
129O shape ring (second elastomer)
Embodiment
Below, utilize illustrated mode of execution to describe this invention in detail.
(first mode of execution)
Fig. 1 represents the cross-sectional view of first mode of execution of the gate rotor of this invention and screw compressor.This screw compressor is single-screw compressor, comprising: the housing 1 with cylinder body 10; The cylindraceous screw rotor 2 chimeric with this cylinder body 10; With with the gate rotor 3 of this screw rotor 2 engagements.
Above-mentioned screw rotor 2 has a plurality of spiral helicine slot parts 21 at outer circumferential face.Above-mentioned gate rotor 3 is a gyroscope-like, has a plurality of tooth portion 31 in the outer circumferential face gear shape.The above-mentioned slot part 21 of above-mentioned screw rotor 2 is meshing with each other with the above-mentioned tooth portion 31 of above-mentioned gate rotor 3.
Being meshing with each other of above-mentioned screw rotor 2 and above-mentioned gate rotor 3 forms pressing chamber C.That is the space that is divided into for inner face of this pressing chamber C, by the above-mentioned cylinder body 10 of the above-mentioned tooth portion 31 of the above-mentioned slot part 21 of above-mentioned screw rotor 2, above-mentioned gate rotor 3, above-mentioned housing 1.
Above-mentioned gate rotor 3 is with the axle 2a point symmetry of above-mentioned screw rotor 2, and configuration is a pair of about above-mentioned screw rotor 2.Above-mentioned housing 1, at the arranged outside gate rotor chamber L of above-mentioned cylinder body 10, this gate rotor chamber L takes in above-mentioned gate rotor 3.Above-mentioned gate rotor chamber L and above-mentioned cylinder body 10 are communicated with by through hole 12.Above-mentioned gate rotor 3 is invaded in the above-mentioned cylinder body 10 from through hole 12.
Above-mentioned screw rotor 2 is the center with above-mentioned axle 2a, in the rotation of arrow R direction, follows the rotation of this screw rotor 2, and above-mentioned gate rotor 3 is the center rotation with axle 3a, compresses the gas in the above-mentioned pressing chamber C.The motor (not shown) of above-mentioned screw rotor 2 by being accommodated in above-mentioned housing 1, rotation.
That is, above-mentioned pressing chamber C, distolateral from the axle 2a direction of above-mentioned screw rotor 2, suck low-pressure gas, compress this low-pressure gas at above-mentioned pressing chamber C, should compressed pressurized gas, from another distolateral ejiction opening 13 ejections of the axle 2a direction that is positioned at above-mentioned screw rotor 2.
Above-mentioned gate rotor 3 has gate rotor main body 30 and the shaft 40 of this gate rotor main body 30 is installed.Above-mentioned gate rotor main body 30 and above-mentioned screw rotor 2 engagements.Above-mentioned shaft 40 is supported on the above-mentioned housing 1.Above-mentioned housing body 30 for example is made of resin, and above-mentioned shaft 40 for example is made of metal.
As shown in Figures 2 and 3, above-mentioned gate rotor main body 30 is discoid, has a plurality of tooth portion 31 of outer circumferential face and is positioned at the hole portion 32 of central authorities.Fig. 2 is the plan view of gate rotor main body, and Fig. 3 is the A-A sectional view of Fig. 2.
As shown in Figure 4 and Figure 5, above-mentioned shaft 40 has: platform portion 43, be arranged on this one 43 one side 43a the first axle part 41 and be arranged on the second axle part 42 of the another side of this one 43.Fig. 4 is the plan view of shaft, and Fig. 5 is the sectional view of the B-B of Fig. 4.
Above-mentioned portion 43 has a plurality of tooth portion 44 at outer circumferential face.This tooth portion 44 is corresponding to the tooth portion 31 of above-mentioned gate rotor main body 30.In addition, in above-mentioned the portion 43 pin-and-hole 45 is set, inserts logical not shown locating stud on this pin-and-hole 45.The axle of above-mentioned the first axle part 41 and the axle of above-mentioned the second axle part 42, consistent with the axle 40a of above-mentioned shaft 40.Above-mentioned the second axle part 42 by bearing, supports above-mentioned housing 1.
As shown in Figure 6 and Figure 7, above-mentioned gate rotor 3, above-mentioned gate rotor main body 30 is supported on the above-mentioned one side 43a of above-mentioned portion 43 of above-mentioned shaft 40.The above-mentioned the first axle part 41 of above-mentioned shaft 40 inserts the above-mentioned hole portion 32 of above-mentioned gate rotor main body 30.Fig. 6 is the plan view of gate rotor, and Fig. 7 is the C-C sectional view of Fig. 6.
On the slit S between the above-mentioned hole portion 32 of the above-mentioned the first axle part 41 of above-mentioned shaft 40 and above-mentioned gate rotor main body 30, configuration elastomer 5.Fig. 6 is for easy understanding, with above-mentioned elastomer 5 blackings.
Above-mentioned elastomer 5 is a leaf spring.This leaf spring is the wavy spring of ring-type.The mountain portion of this wavy spring is positioned at outer circumferential face, and the paddy portion of this wavy spring is positioned at inner peripheral surface.The inner peripheral surface of the above-mentioned hole portion 32 of the mountain portion of this wavy spring and above-mentioned gate rotor main body 30 contacts, and the paddy portion of this wavy spring contacts with the outer circumferential face of the above-mentioned the first axle part 41 of above-mentioned shaft 40.In addition, though not shown, this leaf spring also can be spiral spring.
The above-mentioned elastomer 5 common application of forces are so that the axle 30a of above-mentioned gate rotor main body 30 is consistent with the axle 40a of above-mentioned shaft 40.To above-mentioned gate rotor main body 30 application of forces, the antagonism of the elastic force of above-mentioned gate rotor main body 30 and above-mentioned elastomer 5 is moved in above-mentioned portion 43 of above-mentioned shaft 40 from the outside.
The pin-and-hole 33 of above-mentioned gate rotor main body 30, overlapping with the pin-and-hole 45 of above-mentioned shaft 40, make that mutual axle is consistent, insert logical not shown locating stud.
According to the gate rotor 3 of said structure, the above-mentioned elastomer 5 of configuration between the hole portion 32 of the axial region 41 of above-mentioned shaft 40 and above-mentioned gate rotor main body 30, thus, above-mentioned gate rotor main body 30 can be slided in above-mentioned portion 43 of above-mentioned shaft 40.
Therefore, in screw compressor, use this gate rotor 3, tooth portion 31 and screw rotor 2 engagements with above-mentioned gate rotor main body 30, and under the situation of the above-mentioned shaft 40 of housing 1 upper support, in the running of compressor, it is big that the thermal expansion of above-mentioned screw rotor 2 becomes, on the other hand, the thermal expansion of above-mentioned housing 1 is little, change between the axle 3a of the axle 2a of above-mentioned screw rotor 2 and above-mentioned gate rotor 3 (that is, the axle 40a of above-mentioned shaft 40), even so, above-mentioned gate rotor main body 30 is slided in above-mentioned portion 43 of above-mentioned shaft 40, and the position relation of above-mentioned screw rotor 2 and above-mentioned gate rotor main body 30 is kept suitable distance.
This result can prevent the above-mentioned screw rotor 2 of above-mentioned gate rotor main body 30 intrusions, reduces the breakage of above-mentioned gate rotor main body 30, prevents that the ability of compressor from reducing.In addition, above-mentioned gate rotor main body 30 and above-mentioned screw rotor 2 are powerful mutually presses subsidiary next useless power to reduce.In addition, by above-mentioned elastomer 5 crimp force of above-mentioned gate rotor main body 30 and above-mentioned screw rotor 2 is remained on not degree from above-mentioned pressing chamber C gas leakage.
Therefore, in the running of compressor,, also can prevent gate rotor 3 intrusion screw rotors 2, reduce the breakage of gate rotor 3, prevent that the ability of compressor from reducing by simple structure even because the temperature difference of housing 1 and screw rotor 2 causes gate rotor 3 bendings.
In addition, above-mentioned elastomer 5 is a leaf spring, and above-mentioned elastomer 5 can simply constitute.In addition, above-mentioned leaf spring is the wavy spring or the spiral spring of ring-type, and above-mentioned leaf spring can simply constitute.
Screw compressor according to said structure, possesses above-mentioned gate rotor 3, in the running of compressor, even because the temperature difference of housing 1 and screw rotor 2 causes gate rotor 3 bendings, also can prevent gate rotor 3 intrusion screw rotors 2 by simple structure, reduce the breakage of gate rotor 3, prevent that the ability of compressor from reducing.
(second mode of execution)
Fig. 8 represents second mode of execution of the gate rotor of this invention.The point different with above-mentioned first mode of execution is described, this second mode of execution, elastomeric structure difference.In addition, with the identical symbol of above-mentioned first mode of execution, for the identical structure of above-mentioned first mode of execution, omit its explanation.
The gate rotor 3A of this second mode of execution, elastomer 5A are ring-shaped rubber.The outer circumferential face of this ring-shaped rubber contacts with the inner peripheral surface of the above-mentioned hole portion 32 of above-mentioned gate rotor main body 30, and the inner peripheral surface of this ring-shaped rubber contacts with the outer circumferential face of the above-mentioned the first axle part 41 of above-mentioned shaft 40.
Above-mentioned elastomer 5A, usually the application of force makes the spool consistent of the axle of above-mentioned gate rotor main body 30 and above-mentioned shaft 40.To above-mentioned gate rotor main body 30 application of forces, the elastic force of the above-mentioned elastomer 5A of above-mentioned gate rotor main body 30 antagonism moves on above-mentioned shaft 40 from the outside.
Thus, on the basis of the action effect of above-mentioned first mode of execution, above-mentioned elastomer 5A is the rubber of ring-type, can simply constitute above-mentioned elastomer 5A.
In addition, this invention is not limited to above-mentioned mode of execution, and for example the axial region of the shaft of gate rotor is one, the gate rotor main body is installed on this axial region, and this axial region is supported on the housing also passable.In addition, also can increase and decrease the quantity of gate rotor.
(the 3rd mode of execution)
Then, with reference to accompanying drawing, the 3rd mode of execution of screw compressor of the present invention is described.
At present, exist and to possess the screw rotor with spiral helicine groove, screw compressor with gate rotor of a plurality of teeth that mesh with this spiral helicine groove.How by the synthetic resin manufacturing, there is the problem of the loss of the tooth that reduces gate rotor in this gate rotor.
At this, screw compressor as No. 4890989 communique of U. S. Patent, motion has: support on (support) at the gate rotor that supports gate rotor, in order to give degrees of freedom in sense of rotation, around the pin that floats, use spring, make the gate rotor that supports with respect to gate rotor to the action of relative sense of rotation structure easily.
But the screw compressor complex structure all has boundary in parts precision geometrically and combination precision, and existence can't be ignored the situation in the slit between the groove of the tooth of gate rotor and screw rotor, also has this slit situation in a mess.Slit confusion reigned between the groove of the tooth of such gate rotor and screw rotor, the structure of the screw compressor of above-mentioned document can't absorb the confusion in slit.
In addition, on-stream, the thermal expansion of the tooth of gate rotor and load change, the odontotripsis of resinous gate rotor causes performance low.Particularly, the tooth of gate rotor, height over width is big usually, and the elongation to short transverse during thermal expansion is big.Because the elongation of the teeth directional radial direction of gate rotor, the tooth front end of gate rotor are worn and torn easily at the interior wall friction of the groove of screw rotor.The tooth of the gate rotor that such thermal expansion brings produces elongation, in the structure of the screw compressor of above-mentioned document, can not absorb the elongation of tooth.
At this, following Xu Shu the 3rd mode of execution, the screw compressor that the performance that provides the wearing and tearing that can suppress gate rotor and wearing and tearing to bring reduces.
The structure of＜single-screw compressor 101 〉
The single-screw compressor 101 that Fig. 9～Figure 15 represents comprises: the gate rotor rotating shaft 108,109 of screw rotor 102, the housing 103 of taking in screw rotor 102, the rotating shaft 104 that becomes the running shaft of screw rotor 102, two gate rotors 105,106, the traction bearing that supports from the axle direction of screw rotor 102 107, two gate rotor 105,106 usefulness.
The columned rotor of screw rotor 102 a plurality of spiral helicine grooves 111 for outer circumferential face has.Screw rotor 102 and rotating shaft 104 one can rotate in the inside of housing 103.Screw rotor 102 is by traction bearing 107, and is supported from the direction (opposite direction of the suction direction F1 of gas) of ejection side direction suction side along axle direction.One end of rotating shaft 104 engages with screw rotor 102, and the other end is connected with the driving motor (not shown) of housing 103 outsides.
Two gate rotors, that is, first gate rotor 105 and second gate rotor 106 any, for forming opening 121 in central authorities, the solid of rotation of a plurality of teeth 112 of groove 111 engagements of radial configuration and screw rotor 102 around opening 121 can be around gate rotor rotating shaft 108,109 rotations.
The gate rotor 105,106 of the 3rd mode of execution is by the synthetic resin manufacturing.At this, from the relation of using at screw compressor 101, preferred resistance to pressure, the synthetic resin that rub resistance is high are made gate rotor 105,106.
The opening separately 121 of two gate rotors 105,106, the support gate rotor 105,106 that can rotate freely are inserted in gate rotor rotating shaft 108,109.Specifically, gate rotor rotating shaft 108,109 has the gate rotor support 127 of supporting gate rotor 105,106.It is 127 fixing coaxial with respect to gate rotor rotating shaft 108,109 that gate rotor supports, and gate rotor supports 127 and is similar figures almost with gate rotor 105,106, has smaller size.Gate rotor 105,106 is fixing by pin 124 to support 127 modes that can not rotate with respect to gate rotor.Gate rotor rotating shaft 108,109 is with respect to rotating shaft 104 quadratures of screw rotor 102.
The tooth 112 of gate rotor 105,106, by the slit 114 that on housing 103, forms, can with spiral helicine groove 111 engagements of the screw rotor 102 of the inside of housing 103.Two gate rotors 105,106 are with respect to the rotating center bilateral symmetry configuration of screw rotor 102.In addition, also balanced configuration up and down of gate rotor 105,106.
If screw rotor 102 rotations, then a plurality of teeth 112 of first gate rotor 105 and second gate rotor 106 can mesh with a plurality of grooves 111 successively.
Gate rotor rotating shaft 108,109 is inserted into the opening 121 of gate rotor 105,106 under the state with slit 122.The support gate rotor 105,106 that gate rotor rotating shaft 108,109 can rotate freely.
As the first elastomeric coil spring 128, be configured between the slit 122 of the opening 121 of gate rotor 105,106 and gate rotor rotating shaft 108,109.
And, as second elastomeric O shape ring 129, be configured in be used for stopping gate rotor 105,106 around a plurality of spline pins 123,124 of the rotation of gate rotor rotating shaft 108,109 at least one unsteady pin 124 around.
So, form slit (gap) 122 around the gate rotor rotating shaft 108,109, by at the coil springs 128 of the configuration of the slit 122 around the gate rotor rotating shaft 108,109 and the O shape ring 129 around the pin 124 that floats, can absorb the elongation of footpath direction of the tooth 112 of gate rotor 105,106.
At this, slit between the inwall of the tooth front end of the tooth 112 of gate rotor 105,106 and the groove 111 of screw rotor 102, it is the adjustment in front end slit, in inlet temperature when low load operation or the normal temperature (ambient temperature), be adjusted into the inwall butt of the groove 111 of the tooth front end of tooth 112 of gate rotor 105,106 and screw rotor 102.
Be disposed at the coil spring 126 in slit 122, with respect to gate rotor 105,106 parts, 1 guide finger 123 in a plurality of spline pins 123,124 applies elastic force towards the radial direction of gate rotor 105,106.Thus, for by the tooth 112 that move of guide finger 123 constraints, can effectively absorb the elongation of radial direction by coil spring 126 to radial direction.
Float and sell 124, have under the state that swims than other spline pin (guide finger 123), connect between gate rotor rotating shaft 108,109 and the gate rotor 105,106.
Therefore, one of two spline pins float pin 124 can be more movable than another guide finger 123, can absorb the elongation of footpath direction of the tooth 112 of gate rotor 105,106.
The float play (movably) of radial direction of gate rotor 105,106 of pin 124, the extending amount for the thermal expansion of the radial direction of the tooth that can absorb gate rotor 105,106 brings is set in about 0.1～0.8mm.If not enough 0.1mm then can not be by the elongation that fully absorbs tooth 112 of moving of the pin 124 that floats, if surpass then can the exert an influence problem of rotation smoothly of gate rotor 105,106 of 0.8mm.
As second elastomeric O shape ring 129, being configured in the pin 124 that floats around.By this O shape ring 129, can absorb the elongation of footpath direction of the tooth 112 of gate rotor 105,106.
In addition, at the outer circumferential face of housing 103,, distinguish 1 of opening corresponding to first gate rotor 105 and second gate rotor 106 at the ejection port one 10 that the compressed cold media air of housing 103 inner ejections are used.
These ejiction openings 110 are when screw rotor 102 rotation, in the mode of the groove 111 that can be communicated with screw rotor 102 outer circumferential faces, at the suitable location opening of the outer circumferential face of housing 103.
The action specification of＜single-screw compression molding machine 101 〉
Single-screw compressor 101 following pressurized gass shown in Fig. 9～15.
At first, the rotary driving force that rotating shaft 104 is accepted from the motor (not shown) of housing 103 outsides, screw rotor 102 is in the direction rotation of arrow R1 (with reference to Fig. 9).At this moment, with two gate rotors 105,106 of spiral helicine groove 111 engagement of screw rotor 102, push the inwall of spiral helicine groove 111 by this tooth 112, in the direction rotation of arrow R2.At this moment, side in face of the paper of the screw rotor 102 of Fig. 9～10, the groove 111 of the inner face of housing 103, screw rotor 102, the tooth 112 of gate rotor 105 separate the volume reducing of the pressing chamber of side in face of the paper of formation.And, the paper inboard of screw rotor 102, the groove 111 of the inner face of housing 103, screw rotor 102, the tooth 112 of gate rotor 106 separate the volume reducing of pressing chamber of the paper inboard of formation.
Utilize the minimizing of the volume of these two pressing chambers, refrigerant F1 (with reference to Figure 10) before the compression that the suction side opening 115 of housing 103 imports, before groove 111 and tooth 112 engagements, import pressing chamber, the volume reducing of pressing chamber during groove 111 and tooth 112 engagements, refrigerant is compressed, and thereafter, opens after the engagement of groove 111 and tooth 112, compressed refrigerant F2 (with reference to Figure 10), from gate rotor 105,106 respectively in face of the paper of corresponding Figure 10 in side and the paper ejection port one 0 of side opening spray.
The feature of＜the three mode of execution 〉
(1)
The screw compressor 101 of the 3rd mode of execution, around gate rotor rotating shaft 108,109, form slit 122, by at the coil springs 128 of the configuration of the slit 122 around the gate rotor rotating shaft 108,109 and the O shape ring 129 around the pin 124 that floats, can absorb the elongation of footpath direction of the tooth 112 of gate rotor 105,106.Thus, the tooth front end of the tooth 112 of gate rotor 105,106 is smeared tea at the inwall of the groove 111 of screw rotor 102 can not produce wearing and tearing yet, can prevent the loss of gate rotor 105,106.
(2)
In addition, can manage the slit between the inwall of groove 111 of the tooth front end of tooth 112 of gate rotor 105,106 and screw rotor 102, i.e. the front end slit.For example, corresponding to the conversion of operating condition, the front end slit also can be adjusted automatically.Thus, the performance that can prevent screw compressor 101 reduces.
(3)
And the degrees of freedom height of the machining accuracy of screw compressor 101 and combination precision can reduce manufacture cost.
(4)
And, as the cold media air of pressurized gas etc. is that liquid condition imports screw compressor 101, it is the hydraulic pressure state that contracts, even under the situation of the load change on the tooth 112 of gate rotor 105,106, burning of producing between the inordinate wear of the tooth 112 of gate rotor 105,106, gate rotor 105,106 and the screw rotor 102 also can prevent.Thus, can improve the reliability of screw compressor 101.
For example, possess the opening 121 of gate rotor 105,106 and the slit 122 of gate rotor rotating shaft 108,109, the O shape ring 129 that is configured in the coil spring 128 on this slit 122 and floats and sell configuration around 124, gate rotor 105,106 can move at radial direction, thus, contract even produce unusual hydraulic pressure, the refrigerant of liquid status also can be from the front end escaping slot to screw compressor 101 outside.
(5)
Moreover, the screw compressor 101 of the 3rd mode of execution, in the slit 122 the configuration coil springs 126 with respect to gate rotor 105,106, the part give elastic force towards guide finger 123 to the radial direction of gate rotor 105,106.Therefore, the tooth 112 that moves to radial direction by guide finger 123 constraint can effectively be absorbed the elongations of radial directions by coil spring 126.
(6)
The screw compressor 101 of the 3rd mode of execution, in a plurality of spline pins 123,124 one, for having the unsteady pin 124 that connects under the state that swims than other spline pin (guide finger 123) between gate rotor rotating shaft 108,109 and the gate rotor 105,106, therefore, floating pin 124 can be than guide finger 123 movability more, thus, can absorb the elongation of footpath direction of the tooth 112 of gate rotor 105,106.
(7)
The screw compressor 101 of the 3rd mode of execution as second elastomeric O shape ring 129, is ring-type, being configured in around the pin 124 that floats, and therefore can absorb the elongation of footpath direction of the tooth 112 of gate rotor 105,106.
In addition,, the size and the material of O shape ring 129 can be suited to change, the life-span of gate rotor 105,106 can be prolonged corresponding to the elongation of the footpath direction of the tooth 112 of gate rotor 105,106 and the wear condition of tooth front end.
The variation of＜the three mode of execution 〉
(A)
Above-mentioned the 3rd mode of execution has been enumerated and has been had two kinds of elastomers, promptly describes at the coil springs 128 of 122 configurations of the slit around the gate rotor rotating shaft 108,109 and the structure of the O shape ring 129 around the pin 124 that floating, but the invention is not restricted to this.
As variation of the present invention, possesses any elastomer, promptly the coil springs 128 of the configuration of the slit 133 around the gate rotor rotating shaft 108,109 and the O shape ring 129 around the pin 124 that floating any structure also can, also can absorb the elongation of footpath direction of the tooth 112 of gate rotor 105,106.
(B)
Above-mentioned the 3rd mode of execution is an example with the elastomer that disposes on the slit 122 of the present invention, has enumerated coil spring 126 and has described, but the invention is not restricted to this, and is also passable with elastomer-filled slit 122 integral body of ring-type.In this case, in the full week of gate rotor 105,106, can absorb the elongation of footpath direction of the tooth 112 of gate rotor 105,106.
In addition, elastomer-filled slit 122 integral body of ring-type can further prolong life-span of the tooth 112 of gate rotor 105,106.
Industrial applicibility
The present invention can be used widely in the screw compressor that possesses screw rotor and gate rotor.
Claims (10)
1. a gate rotor is characterized in that, comprising:
Gate rotor main body (30); With
The shaft (40) of this gate rotor main body (30) is installed,
Described gate rotor main body (30) comprise a plurality of tooth portions (31) and be positioned at central authorities hole portion (32),
Described shaft (40) comprises platform portion (43) and axial region (41), described portion (43) is in its one side described gate rotor main body of (43a) upper support (30), the described one side (43a) that described axial region (41) is arranged on described portion (43) goes up and is inserted into described hole portion (32)
Between the hole portion (32) of the axial region (41) of described shaft (40) and described gate rotor main body (30), dispose elastomer (5,5A).
2. gate rotor as claimed in claim 1 is characterized in that:
Described elastomer (5) is a leaf spring.
3. gate rotor as claimed in claim 2 is characterized in that:
Described leaf spring is the wavy spring or the spiral spring of ring-type.
4. gate rotor as claimed in claim 1 is characterized in that:
Described elastomer (5A) is the rubber of ring-type.
5. a screw compressor is characterized in that, comprising:
Housing (1) with cylinder body (10);
The cylindraceous screw rotor (2) chimeric with this cylinder body (10); With
With each described gate rotor in the claim 1～4 of this screw rotor (2) engagement (3,3A),
Described gate rotor (3, the tooth portion of described gate rotor main body (30) 3A) and described screw rotor (2) engagement,
(3, described shaft (40) 3A) is supported by described housing (1) described gate rotor.
6. a screw compressor (101) is characterized in that, comprising:
Screw rotor (102), it has a plurality of spiral helicine grooves (111) and can rotate freely at outer circumferential face;
Gate rotor (105,106), it is formed with opening (121) in central authorities, and disposes the tooth (112) of groove (111) engagement of a plurality of and described screw rotor (102) around described opening (121) radially;
Gate rotor rotating shaft (108,109), it is inserted into the opening (121) of described gate rotor (105,106) with the state with slit (122); With
Elastomer (128,129), it is configured in the opening (121) and the slit (122) between the described gate rotor rotating shaft (108,109) of described gate rotor (105,106), and/or be configured in be used for stopping described gate rotor (105,106) around a plurality of spline pins of the rotation of described gate rotor rotating shaft (108,109) at least one around.
7. screw compressor as claimed in claim 6 (101) is characterized in that:
At the elastomer (128) of described slit (122) configuration, with respect to 1 elastic force that apply to the radial direction of described gate rotor (105,106) of described gate rotor (105,106) in a plurality of described spline pins.
8. screw compressor as claimed in claim 6 (101) is characterized in that:
The elastomer that is configured in the described slit (122) is a ring-type, this elastomer-filled whole described slit (122).
9. as each described screw compressor (101) in the claim 6～8, it is characterized in that:
In a plurality of described spline pins 1 is the pin that floats, and described unsteady pin is for being attached between described gate rotor rotating shaft and the described gate rotor comparing with the state with play with other spline pin.
10. screw compressor as claimed in claim 9 (101) is characterized in that:
Described elastomer (129) is a ring-type, is configured in as around the described spline pin of described unsteady pin.
Applications Claiming Priority (7)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2007-334921 | 2007-12-26 | ||
| JP2007334921 | 2007-12-26 | ||
| JP2007336124 | 2007-12-27 | ||
| JP2007-336124 | 2007-12-27 | ||
| JP2008-319642 | 2008-12-16 | ||
| JP2008319642A JP2009174520A (en) | 2007-12-26 | 2008-12-16 | Gate rotor and screw compressor |
| PCT/JP2008/073523 WO2009081962A1 (en) | 2007-12-26 | 2008-12-25 | Gate rotor and screw compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101918716A true CN101918716A (en) | 2010-12-15 |
Family
ID=40801262
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2008801228982A Pending CN101918716A (en) | 2007-12-26 | 2008-12-25 | Gate rotor and screw compressor |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20110165009A1 (en) |
| EP (1) | EP2236832A4 (en) |
| JP (1) | JP2009174520A (en) |
| CN (1) | CN101918716A (en) |
| WO (1) | WO2009081962A1 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105849412A (en) * | 2014-01-29 | 2016-08-10 | 三菱电机株式会社 | Screw compressor |
| CN107654380A (en) * | 2017-11-14 | 2018-02-02 | 江西红海力能源科技有限公司 | A kind of single screw compressor spider piece |
| CN107701441A (en) * | 2017-11-14 | 2018-02-16 | 江西红海力能源科技有限公司 | A kind of new type single screw compressor spider piece |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101832267A (en) * | 2010-04-28 | 2010-09-15 | 北京力通高科技发展有限公司 | Energy-saving single-screw compressor |
| US9057373B2 (en) | 2011-11-22 | 2015-06-16 | Vilter Manufacturing Llc | Single screw compressor with high output |
| JP6618638B2 (en) * | 2016-12-19 | 2019-12-11 | 三菱電機株式会社 | Single screw compressor and refrigeration air conditioner equipped with the same |
| JP7481660B2 (en) * | 2022-03-28 | 2024-05-13 | ダイキン工業株式会社 | Screw compressors and refrigeration equipment |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4036567A (en) * | 1974-04-15 | 1977-07-19 | Hokuetsu Kogyo Co., Ltd. | Globoid worm type rotary machine |
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| FR2148677A5 (en) * | 1971-07-30 | 1973-03-23 | Zimmern Bernard | |
| JPS5410123B2 (en) * | 1973-10-09 | 1979-05-01 | ||
| JPS5629119B2 (en) * | 1974-04-03 | 1981-07-06 | ||
| JPS611770U (en) * | 1984-06-12 | 1986-01-08 | トヨタ自動車株式会社 | Backless gear device |
| DE3676711D1 (en) * | 1986-07-11 | 1991-02-07 | Willimczik Wolfhart | DISPLACEMENT MACHINE. |
| FR2611000B1 (en) * | 1987-02-12 | 1991-08-16 | Zimmern Bernard | FLOATING PINION WITH SPRING FOR VOLUMETRIC MACHINE |
| US5111712A (en) * | 1988-10-06 | 1992-05-12 | Carrier Corporation | Rolling element radial compliancy mechanism |
| FR2733549A1 (en) * | 1995-04-28 | 1996-10-31 | Zimmern Bernard | SCREW COMPRESSOR WITH LIQUID IMPACT PROTECTION |
| JP3731399B2 (en) | 1999-08-30 | 2006-01-05 | ダイキン工業株式会社 | Screw compressor |
| JP4735197B2 (en) * | 2005-11-04 | 2011-07-27 | 株式会社デンソー | Motor actuator |
| US8328202B2 (en) * | 2007-12-07 | 2012-12-11 | Bal Seal Engineering, Inc. | Seal assembly for high pressure dynamic and static services |
-
2008
- 2008-12-16 JP JP2008319642A patent/JP2009174520A/en active Pending
- 2008-12-25 WO PCT/JP2008/073523 patent/WO2009081962A1/en active Application Filing
- 2008-12-25 US US12/809,159 patent/US20110165009A1/en not_active Abandoned
- 2008-12-25 EP EP08865298.7A patent/EP2236832A4/en not_active Withdrawn
- 2008-12-25 CN CN2008801228982A patent/CN101918716A/en active Pending
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4036567A (en) * | 1974-04-15 | 1977-07-19 | Hokuetsu Kogyo Co., Ltd. | Globoid worm type rotary machine |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105849412A (en) * | 2014-01-29 | 2016-08-10 | 三菱电机株式会社 | Screw compressor |
| CN105849412B (en) * | 2014-01-29 | 2017-07-18 | 三菱电机株式会社 | Helical-lobe compressor |
| CN107654380A (en) * | 2017-11-14 | 2018-02-02 | 江西红海力能源科技有限公司 | A kind of single screw compressor spider piece |
| CN107701441A (en) * | 2017-11-14 | 2018-02-16 | 江西红海力能源科技有限公司 | A kind of new type single screw compressor spider piece |
| CN107654380B (en) * | 2017-11-14 | 2019-01-29 | 江西红海力能源科技有限公司 | A kind of single screw compressor spider piece |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2236832A4 (en) | 2015-01-28 |
| WO2009081962A1 (en) | 2009-07-02 |
| US20110165009A1 (en) | 2011-07-07 |
| JP2009174520A (en) | 2009-08-06 |
| EP2236832A1 (en) | 2010-10-06 |
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Application publication date: 20101215 |