CN108291541A - Convolute-hydrodynamic mechanics - Google Patents
Convolute-hydrodynamic mechanics Download PDFInfo
- Publication number
- CN108291541A CN108291541A CN201680067184.0A CN201680067184A CN108291541A CN 108291541 A CN108291541 A CN 108291541A CN 201680067184 A CN201680067184 A CN 201680067184A CN 108291541 A CN108291541 A CN 108291541A
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- China
- Prior art keywords
- revolution
- pin
- vortex ring
- scroll
- scroll plate
- Prior art date
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Classifications
-
- 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
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
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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
- F01C17/06—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements
-
- 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
- F01C17/06—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements
- F01C17/066—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements with an intermediate piece sliding along perpendicular axes, e.g. Oldham coupling
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0021—Systems for the equilibration of forces acting on the pump
-
- 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
- F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
- F04C29/0064—Magnetic couplings
-
- 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
- F04C2240/80—Other components
- F04C2240/807—Balance weight, counterweight
Abstract
It is an object of the present invention in the constant convolute-hydrodynamic mechanics of the radius of gyration of revolution scroll plate, it will act as preventing the pin of free-wheeling system from reliably engaging with connecting hole (ring).The scroll compressor (10) of the present invention has：Fixed scroll (24)；Scroll plate (22) is turned round, revolution rotary motion is carried out relative to fixed scroll (24)；Main shaft (14) has the input shaft (14a) transmitted for driving force and turns round the eccentric shaft (14c) of scroll plate (22) relative to the eccentric specified amount of input shaft (14a) and transferring a driving force to；And lock ring mechanism (27), it is set between revolution scroll plate (22) and shell (11), prevents the rotation of revolution scroll plate (22).The radius of gyration of the eccentric shaft (14c) of main shaft (14) is being set as ρ s by lock ring mechanism (27), when the radius of gyration of the pin (27a) determined by pin (27a) and ring (27b) is set as ρ pin, meet ρ s<ρpin.
Description
Technical field
The present invention relates to it is a kind of have so-called pin ring prevent free-wheeling system, be used as compressor, expanding machine, stream
The convolute-hydrodynamic mechanics of body pump etc..
Background technology
Convolute-hydrodynamic mechanics have fixed scroll and revolution scroll plate.Fixed scroll and revolution scroll plate exist
One surface side of disk-shaped end plate is equipped with the vortex ring of vortex shape.Make this fixed scroll and revolution scroll plate so that vortex ring engages
State it is opposed, so that revolution scroll plate is carried out revolution rotary motion relative to fixed scroll.Then, by making to be formed in both sides
Scroll plate between compression stroke volume with revolution scroll plate revolution and reduce, in this space fluid carry out
Compression.
As one of the mechanism of rotation for preventing revolution scroll plate, free-wheeling system is prevented there is known pin ring.Pin-ring
Formula prevents free-wheeling system from making multiple pin cards together in corresponding multiple rings to prevent the rotation of revolution scroll plate.Ring can be by as circle
The annular distance in the gap of tubular replaces.
About the convolute-hydrodynamic mechanics for preventing free-wheeling system for having the pin ring, patent document 1 is proposed with by pin
The radius of gyration ρ s of the pin determined with ring become to engage with the vortex ring face for turning round scroll plate than the vortex ring face by fixed scroll
Ring or pin are made revolution by the mode big theoretical radius of gyration ρ th of determining revolution scroll plate to set the internal diameter of ring
The scroll plate direction reduced relative to the torsion of fixed scroll is staggered.
According to patent document 1, becomes bigger than theoretical radius of gyration ρ th due to being set as radius of gyration ρ s, can prevent
The vortex ring face of fixed scroll becomes not engage with the vortex ring face of revolution scroll plate.Further, since ring or pin make revolution be vortexed
The disk direction reduced relative to the torsion of fixed scroll is staggered, therefore the torsion for turning round scroll plate can be suppressed to irreducible minimum
Degree.
Existing technical literature
Patent document
Patent document 1：No. 4745882 bulletins of Japanese Patent No.
Patent document 2：Japanese Patent Laid-fair 6-68276 bulletins (Fig. 2)
Patent document 3：Japanese Patent Laid-Open 2000-230487 bulletins (Fig. 4)
Invention content
Problems to be solved by the invention
For convolute-hydrodynamic mechanics, there is known the construction that the radius of gyration of revolution scroll plate can be made variable and will turn round partly
Diameter is set as constant construction.The radius of gyration is set as variable convolute-hydrodynamic mechanics centrifugal force to be utilized, compressed fluid
Compression reaction force the vortex ring for turning round scroll plate is pressed into the vortex ring of fixed scroll.In addition, the vortex of patent document 1
Formula fluid machinery has the mechanism that the radius of gyration can be made variable.
When assembling has the convolute-hydrodynamic mechanics for preventing free-wheeling system of pin ring, need to insert pins into the interior of ring
Portion.For example, when pin is set to revolution scroll plate, is located on the shell of convolute-hydrodynamic mechanics, in the situation that the radius of gyration can be changed
Under, even if can be by making revolution scroll plate be adjusted in radial displacement, by pin if existence position deviates between pin and ring
The inside of insertion ring.But in the case where the radius of gyration is constant, the displacement of revolution scroll plate can not be made to be adjusted.
It is recorded according to above, it is an object of the invention to the scroll fluid machines that the radius of gyration in revolution scroll plate is constant
It will act as preventing the pin of free-wheeling system from reliably engaging with connecting hole (ring) in tool.
Technical solution
The convolute-hydrodynamic mechanics of the present invention have：Shell；Fixed scroll；Scroll plate is turned round, with relative to fixed whirlpool
Capstan carries out revolution rotary motion, and the mode of the compression stroke of formation compression fluid carries out group between fixed scroll
It closes；Main shaft with the input shaft inputted for driving force and relative to input shaft bias specified amount and transfers a driving force to revolution
The eccentric shaft of scroll plate；And revolution scroll plate prevents free-wheeling system, is set between revolution scroll plate and shell.
Shell is configured to accommodate fixed scroll, revolution scroll plate, main shaft and prevents free-wheeling system.
For the convolute-hydrodynamic mechanics of the present invention, free-wheeling system is prevented to be inserted into respectively by multiple pins and for multiple pins more
A connecting hole engaging.
In addition, the convolute-hydrodynamic mechanics of the present invention are characterized in that, the radius of gyration of the eccentric shaft of main shaft is being set as ρ
S when the radius of gyration of the pin determined by pin and connecting hole is set as ρ pin, meets ρ s<ρpin.
It, will be by since the radius of gyration of the eccentric shaft of main shaft is being set as ρ s for the convolute-hydrodynamic mechanics of the present invention
When the radius of gyration for the pin that pin and connecting hole determine is set as ρ pin, meet ρ s<ρ pin, therefore in assembling convolute-hydrodynamic mechanics
When, it can reliably insert pins into connecting hole.
The present invention convolute-hydrodynamic mechanics in, preferably pin or connecting hole make revolution scroll plate relative to fixed scroll
The direction that the torsion of disk is reduced is staggered.
The present invention convolute-hydrodynamic mechanics in, preferably fixed scroll and turn round scroll plate at least one party the back of the body
The vortex ring face of side and the vortex ring face of veutro thicken in such a way that the side that gap broadens narrows relative to theoretical curve, with gap
The mode that the side to narrow broadens subtracts thickness relative to theoretical curve.
In the convolute-hydrodynamic mechanics of the present invention, preferably by the vortex ring face of fixed scroll and scroll plate will turned round
When the theoretical radius of gyration of the engagement determination in vortex ring face is set as ρ th, meet ρ s<ρ pin and ρ s<ρth.
In the convolute-hydrodynamic mechanics of the present invention, preferably by the vortex ring face of fixed scroll and scroll plate will turned round
When the theoretical radius of gyration of the engagement determination in vortex ring face is set as ρ th, ρ s<ρpin≤ρth.
In the convolute-hydrodynamic mechanics of the present invention, preferably by the vortex ring face of fixed scroll and scroll plate will turned round
When the theoretical radius of gyration of the engagement determination in vortex ring face is set as ρ th, ρ s<ρth<ρpin.
For the convolute-hydrodynamic mechanics of the present invention, in the case where the theoretical radius of gyration ρ th for turning round scroll plate are constant,
Remarkable result can be obtained.
Advantageous effect
Convolute-hydrodynamic mechanics according to the present invention will be by since the radius of gyration of the eccentric shaft of main shaft is being set as ρ s
When the radius of gyration for the pin that pin and connecting hole determine is set as ρ pin, meet ρ s<ρ pin, therefore can be in assembling convolute-hydrodynamic mechanics
When, it will act as preventing the pin of free-wheeling system from reliably inserting connecting hole.
Description of the drawings
Fig. 1 is the profilograph of the schematic configuration for the convolute-hydrodynamic mechanics for indicating embodiments of the present invention.
Fig. 2 is the figure of the right from the left of Fig. 1, is to indicate the ring of the inner side end set on front housing and set on revolution whirlpool
The figure of the position relationship of the pin of the end face outside of capstan.
Fig. 3 (a) is the figure for indicating to generate the situation of torsion in revolution scroll plate, Fig. 3 (b) be expressed as preventing torsion and
The figure for the situation that the position of ring is staggered.
Fig. 4 is the increasing to vortex ring face preferably used by the convolute-hydrodynamic mechanics of present embodiment, revolution scroll plate
It is thick and subtract the thick figure illustrated.
Fig. 5 is to vortex ring face preferably being used by the convolute-hydrodynamic mechanics of present embodiment, avoiding revolution scroll plate
The figure illustrated with the means of the contact in the vortex ring face of fixed scroll.
Fig. 6 be to it is further preferably being used by the convolute-hydrodynamic mechanics of present embodiment, avoid revolution scroll plate
The figure that vortex ring face is illustrated with the means of the contact in the vortex ring face of fixed scroll.
Fig. 7 be to it is further preferably being used by the convolute-hydrodynamic mechanics of present embodiment, avoid revolution scroll plate
The figure that vortex ring face is illustrated with other means of the contact in the vortex ring face of fixed scroll.
Fig. 8 be to pin can not insertion ring the figure that illustrates of condition.
Specific implementation mode
Hereinafter, being said to the scroll compressor 10 of the example of the convolute-hydrodynamic mechanics as the present invention with reference to attached drawing
It is bright.
As shown in Figure 1, scroll compressor 10 has shell 13, which has procapsid 11 and back casing 12, and
These procapsids 11 and back casing 12 are integrally fastened and fixed by bolt (illustration omitted).Hold in the inside of shell 13
Receiving has the revolution scroll plate 22 for constituting scroll compressor mechanism, fixed scroll 24 etc..
In the inside of procapsid 11, main shaft 14 rotates about axis L1 rotations certainly via base bearing 15 and supplementary bearing 16
Such as supported.Main shaft 14 is made of so-called bent axle, and one end side (left side in Fig. 1) is set as input shaft 14a, the input shaft
14a penetrate through procapsid 11 and it is prominent to one end.The attaching electromagnetic clutch EC around input shaft 14a, so as to power with
The interruption of the belt wheel 18 of the peripheral surface of the path boss portion 11a of the one end of procapsid 11 is rotatably freely set to via bearing 17
It is continuous.In this way, power is passed to belt wheel 18 from external drive sources such as engines (not shown) via V-type band etc..The driving force quilt
It is input to input shaft 14a.
It should be noted that mechanical sealing member 19 is equipped between base bearing 15 and supplementary bearing 16, thus in shell 13
Airtight sealing is carried out between air.
On the other hand, it is equipped with big diameter section 14b in the another side of main shaft 14 (right side in Fig. 1), in the big diameter section
Eccentric shaft 14cs of the 14b integrally provided with the rotation axis L1 bias specified amounts relative to main shaft 14.Then, these main shafts 14
Big diameter section 14b and input shaft 14a is rotatably freely supported in procapsid via base bearing 15 and supplementary bearing 16 respectively
11。
In addition, in eccentric shaft 14c, it is linked with revolution scroll plate 22 via balance bush 20 and driving bearing 21, works as master
When axis 14 rotates, revolution scroll plate 22 carries out revolution rotary motion.
The interval of the central axis L2 of the eccentric shaft 14c and rotation axis L1 of main shaft 14 forms the eccentric shaft 14c's of main shaft
Radius of gyration ρ s.
It is formed in balance bush 20 for removing the uncompensated load generated because revolution scroll plate 22 is by revolution driving
Counterweight 20a, counterweight 20a with revolution scroll plate 22 revolution driving together with turn round.
There are a pair of of the fixed scroll 24 for constituting scroll compressor mechanism 23 and revolution to be vortexed in the inner containment of shell 13
Disk 22.
Fixed scroll 24 has fixed charge method end plate 24a and from the fixation whirlpool of the fixed charge method end plate 24a vortex shapes being uprightly arranged
24b is enclosed, on the other hand, revolution scroll plate 22 has revolution end plate 22a and from the revolution end plate 22a vortex shapes being uprightly arranged
Turn round vortex ring 22b.
Fixed scroll 24 and revolution scroll plate 22 make the amount of the respective center separation radius of gyration, and to fix whirlpool
Circle 24b is embedded in the state that vortex ring 22b offsets one from another 180 degree phase to be engaged is turned round.As a result, two scroll plates 24,
Between 22, symmetrically formation relative to scroll plate by fixed charge method end plate 24a, revolution end plate 22a and fixed vortex ring 24b, return
Turn a pair of of discharge chambe C that vortex ring 22b separates.In discharge chambe C, the refrigerant as fluid is compressed.
Fixed scroll 24 is fixed on the inner surface of back casing 12 via bolt 25.Scroll plate 22 is turned round by being set to main shaft
The eccentric shaft 14c of 14 one end is set to the back side of revolution end plate 22a via balance bush 20 and the driving insertion of bearing 21
Boss portion 26, and link with main shaft 14.
In addition, revolution scroll plate 22 is configured to：The back side of revolution end plate 22a is supported in the thrust for being formed in procapsid 11
Bearing plane 11b prevents free-wheeling system by being installed in being used as between the thrust bearing plane 11b and the back side for turning round scroll plate 22
Pin-ring mechanism 27, revolution scroll plate 22 be prevented from rotation on one side, on one side relative to fixed scroll 24 carry out revolution revolution fortune
It is dynamic.
It should be noted that due to revolution vortex ring 22b caused by contacting with each other and fixing the broken of vortex ring 24b in order to prevent
Damage, the scroll compressor 10 that the radius of gyration of revolution scroll plate 22 is constant are set between revolution vortex ring 22b and fixed vortex ring 24b
There is minim gap.
Pin-the ring mechanism 27 has pin 27a and ring 27b, and is stood in the revolution end plate for turning round scroll plate 22 equipped with that will sell 27a
The pin hole 11c at the back side of the 22a and annular distance 27c for making ring 27b be embedded in procapsid 11.
The interval for selling the central axis L4 of the central axis L3 and ring 27b of 27a forms the pin determined by pin and connecting hole
Radius of gyration ρ pin, pin 27a carries out the rotary motion of radius of gyration ρ pin with the rotary motion of revolution scroll plate 22.
It should be noted that these pin holes 11c and annular distance 27c is circumferentially being set to many places, it is 4 in the present embodiment
Place, but can at 3 at 6 in the range of be configured.
Moreover, the central portion opening in the fixed charge method end plate 24a of fixed scroll 24 has the compressed refrigerant gas of discharge
Discharge port 24c, in discharge port 24c, discharge leaf valve (illustration omitted) is set to fixed charge method end plate 24a.
In addition, the back side of the fixed charge method end plate 24a in fixed scroll 24, with what is be in close contact with the inner surface of back casing 12
Mode is provided with the containment members such as O-ring (illustration omitted), is formed between back casing 12 from the inner space of shell 13
The discharge chamber 29 that (confined space) marks off.The inner space of the shell 13 other than chamber 29 is discharged is as suction as a result,
Enter chamber 30 to function.
In intake chamber 30, the system returned from refrigeration cycle is sucked via the suction inlet (illustration omitted) set on procapsid 11
Refrigerant gas, by the intake chamber 30, refrigerant gas be inhaled into be formed in fixed scroll 24 with revolution scroll plate 22 it
Between discharge chambe C.
It should be noted that the joint surface between procapsid 11 and back casing 12 is equipped with the containment members such as O-ring, by shell
Intake chamber 30 in body 13 is relative to air airtight sealing.
The armature (illustration omitted) being made of magnetic substance is attracted to by electromagnetic clutch EC by the magnetic force of electromagnetic coil 41
The contact surface of rotor 43 makes armature be coupled with 43 one of rotor and carrys out passing power.
Electromagnetic clutch EC opens/closes the energization to electromagnetic coil 41 based on the instruction from external controller.Example
Such as, when air-conditioning device switches to opening state from closed state, based on the instruction unpack from external controller to electromagnetism
The energization of coil 41.So that armature 42 is coupled with 43 one of rotor by the magnetic force of electromagnetic coil 41 as a result, is passed from external drive source
The rotary driving force passed is passed to main shaft 14.
Scroll compressor 10 as constructed as above is acted by following.
The rotary driving force that belt wheel 18 is transferred to from external drive source is input to the defeated of main shaft 14 via electromagnetic clutch EC
Enter axis 14a, main shaft 14 is made to rotate.Then, via balance bush 20, driving lining 14d and driving bearing 21 and main shaft 14
The revolution scroll plate 22 of eccentric shaft 14c connections is prevented from rotation by pin-ring mechanism 27 on one side, on one side relative to fixed scroll
24 carry out revolution rotary motion.It should be noted that the driving mechanism of the main shaft 14 is an example, such as it may be used and will have
There is the electro-motor of rotor and stator as driving source among shell 13, and directly rotate main shaft 14 by the rotor
Mechanism.
Then, by the revolution rotary motion of the revolution scroll plate 22, the refrigerant gas in intake chamber 30 is inhaled into
To the discharge chambe C for the most peripheral for being formed in radial direction.After defined revolution angular position stops sucking, discharge chambe C is at it
Volume moves while circumferential direction and profile height direction are reduced to central side.Refrigerant gas is compressed during this period, when
When discharge chambe C reaches the position being connected to discharge port 24c, discharge leaf valve is open, and gas compressed is expelled to discharge
In chamber 29.The compression refrigerant gas is discharged to by the outlet (illustration omitted) set on back casing 12 outside compressor.
Next, for the scroll compressor 10 of present embodiment, in order to make the pin of pin-ring mechanism 27 in assembling
27a reliably inserts the connecting hole of the inside of ring 27b, the radius of gyration ρ s of the eccentric shaft 14c of main shaft 14 and by pin 27a and ring
The radius of gyration ρ pin for the pin 27a that the connecting hole of 27b determines meet formula (1).
ρs<ρ pin formulas (1)
Hereinafter, being illustrated to the relationship with reference to Fig. 2 and Fig. 8.It should be noted that Fig. 8 shows radius of gyration ρ s and
Radius of gyration ρ pin meet the example of the formula (2) for the relationship being in contrast to this embodiment.
ρs>ρ pin formulas (2)
It is illustrated firstly for Fig. 2.
As previously mentioned, the pin 27a of pin-ring mechanism 27 is fixed on the revolution end plate 22a of revolution scroll plate 22, scroll plate is turned round
22 carry out rotary motion with the revolution of the eccentric shaft 14c of main shaft 14.Therefore, pin 27a is carried out also with the revolution of eccentric shaft 14c
The radius of gyration of rotary motion, pin 27a at this time is ρ s.When assembling scroll compressor 10, if being applicable in this theory, sell
27a can be moved according to the position of revolution scroll plate 22 on the circumference of radius of gyration ρ s.
On the other hand, pin 27a is inserted into ring 27b, that is and it is inserted into the inside of connecting hole, thus constitutes pin-ring mechanism 27,
Since the radius of gyration of the pin 27a in pin-ring mechanism 27 is ρ pin, when assembling scroll compressor 10, pin 27a needs
It falls into the range of radius of gyration ρ pin.Since pin 27a can be moved on the circumference of radius of gyration ρ s, in order to which 27a will be sold
The connecting hole of insertion ring 27b needs to meet radius of gyration ρ pin formulas (1) more such greatly than radius of gyration ρ s.
Fig. 2 is premised on turning round scroll plate 22 and be present in the right side in figure as indicated with dotted arrow.It should
Dotted arrow indicates the case where existence position of revolution scroll plate 22, also identical below.
With formula (1) on the contrary, formula (2), that is if radius of gyration ρ pin are smaller than radius of gyration ρ s, such as Fig. 8 institutes
Show, it can not be by pin 27a insertion rings 27b.
It should be noted that if each component comprising pin 27a, ring 27b can free from errors be made, such as formula (3) institute
Show, even if can be by pin 27a insertion rings 27b if in the case where radius of gyration ρ s are equal with radius of gyration ρ pin.But due to
Be difficult to free from errors make each component in reality, thus present embodiment by radius of gyration ρ pin than radius of gyration ρ s wonderful works
Condition.ρ s=ρ pin ... formulas (3)
As described above, according to the present embodiment, it is by keeping radius of gyration ρ pin bigger than radius of gyration ρ s, pin 27a is reliable
Ground insertion ring 27b (connecting hole), is conducive to the assembling of scroll compressor 10.
It should be noted that for making which kind of degree radius of gyration ρ pin arrive greatly than radius of gyration ρ s, because of scroll compressor
The difference of the size of machine 10 etc. and can not broadly determine, but can be taken on pin 27a and ring 27b and prevent revolution scroll plate 22
It is determined on the basis of the range of this function of rotation.
Specifically, can be set in a manner of meeting formula below (A).
ρpin-ρs<δ m × Rpin/b formulas (A)
ρpin：Sell the radius of gyration of 27a
ρs：The radius of gyration of eccentric shaft 14c
δm：The gap of initial revolution scroll plate 22 and the vortex ring face of fixed scroll 24
b：The basic radius of circle of involute curve
α：Turn round the torsion angle of scroll plate 22 and fixed scroll 24
Rpin：Distance from the center of eccentric shaft 14c to the center of pin 27a or to the center of ring 27b
Above-mentioned formula (A) is illustrated.
Initial fixed scroll 24 and the gap in the vortex ring face of both revolution scroll plates 22 are set as δ m.
For example, when the vortex ring face for being set as fixed scroll 24 and revolution scroll plate 22 is formed by involute curve, if
By its basis, radius of circle is set as b, and the torsional capacity of fixation/revolution scroll plate is set as α (rad), then fixed scroll is vortexed with revolution
One side (fixed veutro) in the gap of disk reduces the amount of b × α, and another party's (fixed back side) increases the amount of b × α.
Therefore, the maximum permissible value of the torsion of scroll plate needs to meet following formula (B).
δm>B × α formulas (B)
In addition, scroll plate torsion α by initial ρ pin, ρ s setting value Δ (Δ=ρ pin- ρ s) and lock ring setting
Position radius Rpin determines that relationship is indicated with formula (C).
α=Δ/Rpin formulas (C)
Therefore, provide that above-mentioned formula (A) theoretically contacts if meeting the formula (A) by formula (B), (C)
The vortex ring face of scroll plate will not contact.
It should be noted that scroll compressor 10 is equipped with pin 27a in revolution scroll plate 22, ring is equipped in procapsid 11
27b, even if in contrast, being equipped with ring 27b in revolution scroll plate 22, being equipped with pin 27a in procapsid 11 also can equally meet calculation
The relationship of formula (1).In addition, can also form annular distance without using ring 27b.
It in addition to the above, can be to the structure that is enumerated in the above embodiment without departing from the purport of the present invention
At choice selection is carried out, it can also suitably change and be constituted for other.Hereinafter, to can apply to the present invention it is several preferably comprise into
Row explanation.
For scroll compressor 10, with the rotary motion of revolution scroll plate 22, the torque along direction of rotation torsion is made
For turning round scroll plate 22.For example, as shown in Fig. 3 (a), in the case of revolution scroll plate 22 rotation R (clockwise) to dextrorotation,
The moment loading of dextrorotation is in revolution scroll plate 22.Since pin 27a meets formula (1), it is equipped between the inner wall of ring 27b and ρ
The comparable gaps pin- ρ s, therefore the amount that scroll plate 22 rotates this gap relative to fixed scroll 24 is turned round, so will produce
Reverse α.
Between the gap in vortex ring face and the vortex ring face of veutro of the back side of the discharge chambe C fixed scrolls 24 being sealed
Gap changes, and the compression performance of scroll compressor 10 can probably reduced.In addition, as shown in Fig. 3 (a), when revolution is vortexed
For disk 22 when turn-knob turns to the right, the gap in the vortex ring face of the back side of fixed scroll 24 becomes bigger than the gap in the vortex ring face of veutro,
When turn-knob turns revolution scroll plate 22 to the left, the gap in the vortex ring face of the veutro of fixed scroll 24 becomes the vortex ring face than back side
Gap it is big.
Here, the gap in the vortex ring face of the back side of fixed scroll 24 refers to the vortex ring face with the veutro of revolution scroll plate 22
Between gap (being indicated by (3) of Fig. 4, (4)), the gap in the vortex ring face of the veutro of fixed scroll 24 refers to being vortexed with revolution
Gap (being indicated by (1) of Fig. 4, (2)) between the vortex ring face of the back side of disk 22.
Here, as shown in Fig. 3 (b), in the present invention preferably by pin 27a (or ring 27b) in the direction of torsion α reductions
Be staggered the amount of Δ.As a result, by the way that by the amount of dextrorotation reversed turn-knob to the left and return displacement, torsion α is reduced, and can make fixed scroll
The back side in 24 vortex ring face is balanced with the gap of veutro, inhibits the reduction of the compressed capability of scroll compressor 10, and back side
Become more preferable with the balance of the pressure of veutro.
Then and with reverse related composition, but countermeasure on the basis of allowing to generate torsion.
As previously mentioned, when turning round the generation torsion of scroll plate 22, between the veutro and back side of fixed scroll 24
Gap will produce uneven.
For example, as shown in figure 4, when turn round scroll plate 22 turn-knob turns to the left when, the veutro ((1), (2) of fixed scroll 24
Arrow shown in side) gap broaden, the gap turn narrow of back side (side shown in the arrow of (3), (4)).In general, revolution
The veutro and back side of scroll plate 22 and fixed scroll 24 are all in accordance with along the theoretical curve of involute curve (solid line of Fig. 4)
It is formed.Here, in the present embodiment, the shape of back side and veutro is not set as ideal curve by proposition, and be created as with
Reverse the scheme of corresponding shape.That is as in Fig. 4 as double dot dash line indicates, because torsion causes gap to broaden
The veutro of fixed scroll 24 thicken (24d) relative to theoretical curve in a manner of making gap turn narrow, in contrast, because of torsion
The back side of the fixed scroll 24 of gap turn narrow is caused to subtract thick (24e) relative to theoretical curve in such a way that gap broadens.It needs
Illustrate, Fig. 4 is to indicate to thicken (24d) and subtract thick (24e) as the main purpose, although vortex ring face is each other because thickening (24d)
And subtract thick (24e) and contact, but this is illustrates, and is not the element for limiting the present invention.
It is recorded according to above, the back side that can make fixed scroll 24 is balanced with the gap of veutro, inhibits scroll compressor
The reduction of 10 compressed capability, and the balance of the pressure of back side and veutro becomes more preferable.
Which kind of determined i.e. according to the specification of scroll compressor 10 to degree it should be noted that thickening and subtracting thickness
It can.
Then, as previously mentioned, in the constant scroll compressor 10 of the radius of gyration of revolution scroll plate 22, revolution is vortexed
The revolution vortex ring 22b of disk 22 and the fixation vortex ring 24b needs of fixed scroll 24 are non-contiguously arranged small therebetween
Gap.
Here, as shown in figure 5, present embodiment preferably satisfies ρ s<ρ pin formulas (1) and ρ s<ρth···
Formula (4).It should be noted that ρ th are by the revolution scroll plate for engaging determination of revolution scroll plate 22 and fixed scroll 24
The 22 theoretical radius of gyration.
By meeting formula (4), the contact of revolution scroll plate 22 and fixed scroll 24 can be reliably avoided.
Meeting ρ s<ρ pin formulas (1) and ρ s<In the case of ρ th formulas (4), ρ pin and ρ th's
Relationship can select either one or two of formula below (5) and formula (6).
ρ pin≤ρ th formulas (5)
ρpin>ρ th formulas (6)
It should be noted that when formula (5) is added to formula (1), ρ s can be denoted as<ρ pin≤ρ th formulas
(7), when formula (6) is added to formula (1), ρ s can be denoted as<ρth<ρ pin formulas (8).
The case where having selected formula (5) is shown in FIG. 6, since the torsion of revolution scroll plate 22 can be reduced, can make
The back side of fixed scroll 24 is balanced with the gap of veutro, can steadily operate scroll compressor 10.
In addition, the case where having selected formula (6) is shown in FIG. 7, since revolution scroll plate 22 and fixed scroll can be reduced
The primary clearance δ m of disk 24, therefore the reduced performance of scroll compressor 10 can be inhibited.
In addition to this, a specific example for constituting the only present invention for scroll compressor 10, constitutes vortex pressure
Shape, size of each element of contracting machine etc. are arbitrary.
For example, scroll compressor 10 sells 27a in the revolution setting of scroll plate 22, in fixed scroll 24 by with ring
Connecting hole is arranged in 27b, but also can pin 27a be set to 24 side of fixed scroll, and connecting hole is set to 22 side of revolution scroll plate.The feelings
Connecting hole under condition can also be not provided with ring 27b, and be directly arranged in the revolution end plate 22a of revolution scroll plate 22.
In addition, this embodiment illustrates free-wheeling system is prevented in pin ring, a pin card is together in ring (card
Close hole) mechanism, but the present invention is not limited thereto.Such as shown in patent document 2, multiple (such as two) pin can also be applied to
Be sticked in ring prevents free-wheeling system.
In addition, this embodiment illustrates the fixed mechanisms in the position for preventing from selling in free-wheeling system in pin ring, but
The present invention is not limited thereto.Such as shown in patent document 3, the displacement for the radial direction for allowing pin and limitation can also be applied to
Maximum displacement prevents free-wheeling system.
Symbol description
10 scroll compressors
11 procapsids
11a path boss portions
11b thrust bearing planes
11c pin holes
12 back casings
13 shells
14 main shafts
14a input shafts
The big diameter sections of 14b
14c eccentric shafts
14d driving linings
15 base bearings
16 supplementary bearings
17 bearings
18 belt wheels
19 mechanical sealing members
20 balance bushes
20a counterweights
21 driving bearings
22 revolution scroll plates
22a turns round end plate
22b turns round vortex ring
23 scroll compressor mechanisms
24 fixed scrolls
24a fixed charge method end plates
24b fixes vortex ring
24c discharge ports
25 bolts
26 boss portions
27 pins-ring mechanism
27a is sold
27b rings
27c annular distances
28 holders
29 discharge chambers
30 intake chambers
41 electromagnetic coils
43 rotors
C discharge chambes
L1 rotation axis
L2 central axis
L3 central axis
L4 central axis
EC electromagnetic clutch
The ρ pin radius of gyration
The ρ s radius of gyration
Claims (11)
1. a kind of convolute-hydrodynamic mechanics, which is characterized in that have：
Shell；
Fixed scroll；
Turn round scroll plate, to carry out revolution rotary motion relative to the fixed scroll, and with the fixed scroll
Between form the mode of compression stroke of compression fluid and be combined；
Main shaft and with the input shaft inputted for driving force and relative to the input shaft bias specified amount pass the driving force
It is handed to the eccentric shaft of the revolution scroll plate；And
The revolution scroll plate prevents free-wheeling system, is set between the revolution scroll plate and the shell,
The shell is configured to accommodate the fixed scroll, the revolution scroll plate, the main shaft and described prevents rotation
Mechanism,
The multiple connecting holes engaging for preventing free-wheeling system to be configured to be inserted into respectively by multiple pins and for the multiple pin,
The radius of gyration of the eccentric shaft of the main shaft is being set as ρ s, described in being determined by the pin and the connecting hole
When the radius of gyration of pin is set as ρ pin,
Meet ρ s<ρpin.
2. convolute-hydrodynamic mechanics according to claim 1, wherein
The pin or the connecting hole are in the direction for keeping the revolution scroll plate reduced relative to the torsion of the fixed scroll
It is staggered.
3. convolute-hydrodynamic mechanics according to claim 1 or 2, wherein
The vortex ring face of the back side of at least one party of the fixed scroll and the revolution scroll plate and the vortex ring face of veutro
Thickened relative to theoretical curve in such a way that the side that gap broadens narrows, in such a way that a side of gap turn narrow broadens relative to
Theoretical curve subtracts thickness.
4. convolute-hydrodynamic mechanics according to any one of claim 1 to 3, wherein
It will turned round with the determining theory that engages in the vortex ring face of the revolution scroll plate by the vortex ring face of the fixed scroll
When radius is set as ρ th,
Meet ρ s<ρ pin and ρ s<ρth.
5. convolute-hydrodynamic mechanics according to any one of claim 1 to 3, wherein
It will turned round with the determining theory that engages in the vortex ring face of the revolution scroll plate by the vortex ring face of the fixed scroll
When radius is set as ρ th,
ρs<ρpin≤ρth。
6. convolute-hydrodynamic mechanics according to any one of claim 1 to 3, wherein
It will turned round with the determining theory that engages in the vortex ring face of the revolution scroll plate by the vortex ring face of the fixed scroll
When radius is set as ρ th,
ρs<ρth<ρpin。
7. convolute-hydrodynamic mechanics according to any one of claim 1 to 6, wherein
The theoretical radius of gyration ρ th of the revolution scroll plate are constant.
8. convolute-hydrodynamic mechanics according to claim 1, wherein
The vortex ring face of the back side of the fixed scroll and the vortex ring face of the veutro phase in such a way that the side that gap broadens narrows
Theoretical curve is thickened, subtracts thickness relative to theoretical curve in such a way that a side of gap turn narrow broadens.
9. convolute-hydrodynamic mechanics according to claim 1, wherein
The vortex ring face of the back side of the revolution scroll plate and the vortex ring face of the veutro phase in such a way that the side that gap broadens narrows
Theoretical curve is thickened, subtracts thickness relative to theoretical curve in such a way that a side of gap turn narrow broadens.
10. convolute-hydrodynamic mechanics according to claim 7, wherein
The vortex ring face of the back side of the fixed scroll and the vortex ring face of the veutro phase in such a way that the side that gap broadens narrows
Theoretical curve is thickened, subtracts thickness relative to theoretical curve in such a way that a side of gap turn narrow broadens.
11. convolute-hydrodynamic mechanics according to claim 7, wherein
The vortex ring face of the back side of the revolution scroll plate and the vortex ring face of the veutro phase in such a way that the side that gap broadens narrows
Theoretical curve is thickened, subtracts thickness relative to theoretical curve in such a way that a side of gap turn narrow broadens.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2015-227465 | 2015-11-20 | ||
| JP2015227465A JP6718223B2 (en) | 2015-11-20 | 2015-11-20 | Scroll fluid machinery |
| PCT/JP2016/004923 WO2017085935A1 (en) | 2015-11-20 | 2016-11-18 | Scroll fluid machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108291541A true CN108291541A (en) | 2018-07-17 |
| CN108291541B CN108291541B (en) | 2020-03-13 |
Family
ID=58719201
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201680067184.0A Active CN108291541B (en) | 2015-11-20 | 2016-11-18 | Scroll fluid machine |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20180328361A1 (en) |
| JP (1) | JP6718223B2 (en) |
| CN (1) | CN108291541B (en) |
| DE (1) | DE112016005318B4 (en) |
| WO (1) | WO2017085935A1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6750548B2 (en) | 2017-03-30 | 2020-09-02 | 株式会社豊田自動織機 | Scroll compressor |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS623101A (en) * | 1985-06-28 | 1987-01-09 | Shin Meiwa Ind Co Ltd | Scroll type fluid machine |
| CN1074276A (en) * | 1991-12-20 | 1993-07-14 | 株式会社日立制作所 | Scroll-type fluid machine, scroll element and processing method thereof |
| JP2000170671A (en) * | 1998-09-29 | 2000-06-20 | Tokico Ltd | Scroll type hydraulic machine |
| CN1366138A (en) * | 2001-01-17 | 2002-08-28 | 三菱重工业株式会社 | Vortex compressor |
| CN101063449A (en) * | 2006-04-28 | 2007-10-31 | 三菱重工业株式会社 | Scroll compressor |
| CN102678550A (en) * | 2011-03-09 | 2012-09-19 | Lg电子株式会社 | Scroll compressor |
| CN203717348U (en) * | 2014-01-23 | 2014-07-16 | 广州日立压缩机有限公司 | Scroll compressor for freezing |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4490099A (en) * | 1980-10-03 | 1984-12-25 | Sanden Corporation | Scroll type fluid displacement apparatus with thickened center wrap portions |
| US5395222A (en) * | 1989-11-02 | 1995-03-07 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor having recesses on the scroll wraps |
| JPH0668276A (en) | 1992-08-20 | 1994-03-11 | Tokimec Inc | Information controller of facility equipment |
| US6224357B1 (en) | 1998-09-29 | 2001-05-01 | Tokioco Ltd. | Scroll fluid machine having an orbiting radius varying mechanism and a clearance between the wrap portions |
| JP4088392B2 (en) | 1998-12-09 | 2008-05-21 | 三菱重工業株式会社 | Scroll type fluid machinery |
| CN1164871C (en) * | 2000-10-23 | 2004-09-01 | Lg电子株式会社 | Scroll compressor |
| JP5180490B2 (en) * | 2007-02-27 | 2013-04-10 | 三菱重工業株式会社 | Scroll compressor |
| JP6207942B2 (en) | 2013-09-19 | 2017-10-04 | サンデンホールディングス株式会社 | Scroll type fluid machinery |
-
2015
- 2015-11-20 JP JP2015227465A patent/JP6718223B2/en active Active
-
2016
- 2016-11-18 CN CN201680067184.0A patent/CN108291541B/en active Active
- 2016-11-18 DE DE112016005318.5T patent/DE112016005318B4/en active Active
- 2016-11-18 WO PCT/JP2016/004923 patent/WO2017085935A1/en active Application Filing
- 2016-11-18 US US15/777,462 patent/US20180328361A1/en not_active Abandoned
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS623101A (en) * | 1985-06-28 | 1987-01-09 | Shin Meiwa Ind Co Ltd | Scroll type fluid machine |
| CN1074276A (en) * | 1991-12-20 | 1993-07-14 | 株式会社日立制作所 | Scroll-type fluid machine, scroll element and processing method thereof |
| JP2000170671A (en) * | 1998-09-29 | 2000-06-20 | Tokico Ltd | Scroll type hydraulic machine |
| CN1366138A (en) * | 2001-01-17 | 2002-08-28 | 三菱重工业株式会社 | Vortex compressor |
| CN101063449A (en) * | 2006-04-28 | 2007-10-31 | 三菱重工业株式会社 | Scroll compressor |
| CN102678550A (en) * | 2011-03-09 | 2012-09-19 | Lg电子株式会社 | Scroll compressor |
| CN203717348U (en) * | 2014-01-23 | 2014-07-16 | 广州日立压缩机有限公司 | Scroll compressor for freezing |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2017096132A (en) | 2017-06-01 |
| CN108291541B (en) | 2020-03-13 |
| DE112016005318T5 (en) | 2018-08-23 |
| US20180328361A1 (en) | 2018-11-15 |
| JP6718223B2 (en) | 2020-07-08 |
| WO2017085935A1 (en) | 2017-05-26 |
| DE112016005318B4 (en) | 2024-03-21 |
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