CN109611332A - A kind of rolling rotor compressor of double atmospheric pressure - Google Patents
A kind of rolling rotor compressor of double atmospheric pressure Download PDFInfo
- Publication number
- CN109611332A CN109611332A CN201710969318.4A CN201710969318A CN109611332A CN 109611332 A CN109611332 A CN 109611332A CN 201710969318 A CN201710969318 A CN 201710969318A CN 109611332 A CN109611332 A CN 109611332A
- Authority
- CN
- China
- Prior art keywords
- rolling
- circle
- center
- rotor
- cylinder
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
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
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/32—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
- F04C18/322—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and reciprocating with respect to the outer member
-
- 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
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The invention discloses a kind of rolling rotor compressors of double atmospheric pressure, including cylinder block, rolling-rotor, camshaft, air entry, spring, slide plate, cylinder drive end bearing bracket, cylinder rear end cap, it is characterized by: the cylindrical surface of rolling-rotor is equipped with high pressure gas hole and low pressure exhaust hole, the end face of rolling-rotor is embedded with cylindrical keys, the eccentric part of camshaft is equipped with the exhaust passage of connection cylinder and an end face, cylinder drive end bearing bracket is equipped with high-pressure exhaust and low pressure exhaust mouth, cylinder drive end bearing bracket medial surface is equipped with radial keyway, cylindrical keys are inserted into radial keyway.The invention has the advantages that making change of the rolling rotor compressor by rolling-rotor, camshaft and cylinder drive end bearing bracket mutual alignment, exhaust passage, height (low) pressure stomata and high whether being connected of (low) pressure port are controlled, double atmospheric pressure is realized.
Description
Technical field
The present invention relates to Compressor Technology fields, more particularly to a kind of rolling rotor compressor of double atmospheric pressure.
Background technique
Rolling rotor compressor has the characteristics that structure is simple, easy to process, is often used as domestic air energy heat pump pressure
Contracting machine.The working principle of traditional rolling rotor compressor is that cylinder inner cavity wall surface, rolling-rotor outer wall and slide plate constitute envelope
The volume of cylinder closed, i.e. element volume, volume size change with rolling-rotor corner, and the pressure of gas is then with primitive in volume
The size of volume and change, to complete the course of work of compressor.It is needing while carrying out heat supply and heating (provides life respectively
Hot water and heating living) in the case where, it is energy saving, it is desirable that compressor should provide two different pressures at expulsion.Traditional rolling
Dynamic rotor-type compressor can only provide a pressure at expulsion, and single device is not able to satisfy the needs of double-exhaust pressure.
Summary of the invention
Double atmospheric pressure cannot be provided in order to overcome the shortcomings of to roll function rotor-type compressor, the present invention provides a kind of dependence
Rolling-rotor, camshaft and the rolling rotor-type compression for changing to realize double atmospheric pressure of cylinder drive end bearing bracket mutual alignment
Machine, the signified double atmospheric pressure of the present invention, compression ratio are low pressure when reaching 1.5~2, and compression ratio (is pressed when reaching 3~4 for high pressure
Contracting is than the ratio for pressure at expulsion and pressure of inspiration(Pi)).
The technical scheme adopted by the invention is that: a kind of rolling rotor compressor of double atmospheric pressure, including cylinder block,
Rolling-rotor, camshaft, air entry, spring, slide plate, cylinder drive end bearing bracket, cylinder rear end cap, it is characterised in that: the rolling
The cylindrical surface of turn is equipped with high pressure gas hole and low pressure exhaust hole, and the end face of rolling-rotor is embedded with cylindrical keys, described
The eccentric part of camshaft is equipped with the exhaust passage of connection cylinder and an end face, and the cylinder drive end bearing bracket is equipped with high pressure
Exhaust outlet and low pressure exhaust mouth, cylinder drive end bearing bracket medial surface are equipped with radial keyway, and the cylindrical keys are inserted into radial keyway.
Further, cylinder block is embedded with positioning pin by cylinder drive end bearing bracket side, and cylinder drive end bearing bracket medial surface is equipped with location hole.
When work, motor driven camshaft is rotated, and the movement of the cylindrical keys on rolling-rotor is because being limited
System is in radial key keyway, so that rolling-rotor has the relative rotation around camshaft eccentric part axle center, and before cylinder
End cap be it is static, the relative position for being finally reached exhaust passage, high pressure and low pressure exhaust hole and high pressure and low pressure exhaust mouth exists
Regular continuous variation in one rotation period.In compression process, exhaust passage, high pressure gas hole (low pressure exhaust hole), high pressure
Exhaust outlet (low pressure exhaust mouth) is not attached to lead to, and ensure that the progress of compression；In low pressure exhaust, only exhaust passage, low pressure exhaust
Hole is connected with low pressure exhaust mouth, ensure that the progress of low pressure exhaust；In high pressure gas, only exhaust passage, high pressure gas hole
It is connected with high-pressure exhaust, ensure that the progress of high pressure gas.By the cooperation of positioning pin and location hole, cylinder block ensure that
It is consistent with design value with relative position of the cylinder drive end bearing bracket in practical set.
Specific design parameter are as follows:
The distance in the inner terminal of radial keyway to the cylinder drive end bearing bracket center of circle is less than the point on camshaft eccentric part cylinder
To the shortest distance in the rotation center of circle, the distance in outermost end to the cylinder drive end bearing bracket center of circle of radial keyway is equal to interior the half of cylinder block
Diameter, that is to say, that the length of radial keyway will ensure that rolling-rotor can rotate a circle in cylinder.When rolling-rotor external cylindrical surface
With the normal at cylinder intracoelomic cavity cylinder point of contact it is parallel with radial keyway when, if the point of contact is far from radial keyway, cylindrical keys fortune
Move the inward flange of radial keyway groove body；If the point of contact moves to radial keyway groove body close to radial keyway, cylindrical keys
Outer edge.
The entrance of exhaust passage is the strip arc deep gouge on the cylinder of the eccentric part of camshaft, exhaust passage
Outlet be the strip arc deep gouge concentric with shaft on the end face of the eccentric part of camshaft.Exhaust passage into
Outlet, which is set as strip, to allow compressor to have time enough to be exhausted.
Camshaft is rotated to point farthest from the camshaft rotation center of circle on the center of circle and camshaft eccentric part cylinder
Wire definition be benchmark line；The stop of Vent passageway arc deep gouge in rotational direction is formed with the camshaft rotation center of circle
Line and the angle of reference line be 40 °, Vent passageway arc deep gouge turns along the stop and camshaft of rotation opposite direction
The angle of line and reference line that the dynamic center of circle is formed is 20 °；The stop of exhaust passage entrance arc deep gouge in rotational direction and partially
It is 35 ° that heart wheel shaft, which rotates the line that the center of circle is formed and the angle of reference line,.
The high pressure gas hole center of circle to cylinder rear end cap distance and the low pressure exhaust hole center of circle to cylinder rear end cap distance phase
Deng, and it is equal to the center line of exhaust passage entrance arc deep gouge to the distance of cylinder rear end cap, to guarantee that camshaft is rotating
In the process, being connected to for exhaust passage entrance and high and low pressure gas vent can be realized respectively.
Included angle of straight line where the line at the high-pressure exhaust center of circle and cylinder drive end bearing bracket center and radial keyway groove body for 135~
165 °, the line and radial keyway groove body place included angle of straight line at the low pressure exhaust mouth center of circle and cylinder drive end bearing bracket center are 20~50 °.
The minimum range at high-pressure exhaust circle upper and on low pressure exhaust mouth circle point to cylinder drive end bearing bracket center is equal, and waits
It, can the row of realization respectively to guarantee camshaft during rotation in the inner arc radius of Vent passageway arc deep gouge
Gas channel outlet is connected to high and low pressure exhaust outlet.
The maximum distance at high-pressure exhaust and point to cylinder drive end bearing bracket center on low pressure exhaust mouth circle is equal, and is less than inclined
Point on heart wheel shaft eccentric part cylinder to the rotation center of circle the shortest distance and rolling-rotor wall thickness and, that is, guarantee without
In the case where exhaust passage, cylinder intracoelomic cavity will not be connected to high-pressure exhaust, low pressure exhaust mouth.
The cylindrical keys center of circle and the rolling-rotor center of circle are formed by line and the high pressure gas hole center of circle and rolling-rotor center
The line angle of formation is 160~190 °, and the cylindrical keys center of circle and the rolling-rotor center of circle are formed by line and low pressure exhaust hole
The line angle that the center of circle and rolling-rotor are centrally formed is 0~20 °.
The equivalent width of the diameter of cylindrical keys and radial keyway, to guarantee movement quilt of the cylindrical keys in radial keyway
Strictly it is limited on single line.
By above design scheme, finally make (low) pressure of the exhaust passage on camshaft, the height on rolling-rotor
Height (low) pressure port on gas vent, cylinder drive end bearing bracket is not attached to lead to when needing to compress；In low pressure exhaust, only eccentric wheel
The low pressure exhaust hole on exhaust passage, rolling-rotor on axis is connected with the low pressure exhaust mouth on cylinder drive end bearing bracket；In high pressure
When exhaust, the only exhaust passage on camshaft, the high pressure gas on high pressure gas hole and cylinder drive end bearing bracket on rolling-rotor
Mouth is connected.
The invention has the advantages that by adopting the above technical scheme, rolling rotor compressor passes through rolling-rotor, bias
The change of wheel shaft and cylinder drive end bearing bracket mutual alignment, control exhaust passage, height (low) pressure stomata and high (low) pressure port
Whether connection, double atmospheric pressure is realized, low pressure at expulsion is for used in heating, used in high pressure at expulsion domestic hot-water supply.
Detailed description of the invention
Fig. 1 is structural schematic diagram of the invention.
Fig. 2 is the structural schematic diagram of rolling-rotor Yu camshaft Relative sliding.
Fig. 3 is cylinder drive end bearing bracket medial surface figure.
Fig. 4 is camshaft schematic diagram.
Fig. 5 is the end view drawing of camshaft.
Fig. 6 is the elevation of camshaft.
Fig. 7 is the elevation of rolling-rotor.
Fig. 8 is the end view drawing of rolling-rotor.
Fig. 9 is air-breathing and compression process schematic diagram.
Figure 10 is that exhaust passage starts to be connected to schematic diagram with low pressure exhaust mouth.
Figure 11 is air-breathing and low pressure exhaust process schematic.
Figure 12 is that low pressure exhaust terminates schematic diagram.
Figure 13 is air-breathing and high pressure compressed process schematic.
Figure 14 is air-breathing and high pressure gas process schematic.
Figure 15 is that high pressure gas terminates schematic diagram.
In figure: 1. cylinder drive end bearing brackets, 2. high-pressure exhausts, 3. suction chambers, 4. air entries, 5. slide plates, 6. springs, 7. compressions
Chamber, 8. high pressure gas holes, 9. cylinder rear end caps, 10. cylinder block, 11. exhaust passages, 12. positioning pins, 13. cylindrical keys, 14.
Rolling-rotor, 15. camshafts, 16. radial keyways, 17. low pressure exhaust holes, 18. low pressure exhaust mouths, 19. location holes.
Specific embodiment
The following further describes the present invention with reference to the drawings.
It please refers to shown in attached drawing 1-8, a kind of rolling rotor compressor of double atmospheric pressure, rolling rotor compressor master
It will be by cylinder block 10, rolling-rotor 14, camshaft 15, air entry 4, spring 6, slide plate 5, cylinder drive end bearing bracket 1, cylinder rear end cap
9, the high pressure gas hole 8 on 14 cylinder of rolling-rotor and low pressure exhaust hole 17, embedded in 14 end face of rolling-rotor cylindrical keys 13,
The high pressure gas being connected on the cylinder of the eccentric part of camshaft 15 and the exhaust passage 11 of an end face, cylinder drive end bearing bracket 1
Mouth 2 and low pressure exhaust mouth 18, the radial keyway 16 of 1 medial surface of cylinder drive end bearing bracket and location hole 19, cylinder block 10 lean on cylinder front end
The positioning pin 12 of 1 side of lid forms.
When work, motor driven camshaft 15 is rotated, the movement of the cylindrical keys 13 on rolling-rotor 14
Because being limited on single line, so that rolling-rotor 14 has relative to camshaft 15 around camshaft eccentric part split axle
The relative rotation of the heart, and cylinder drive end bearing bracket 1 is fixed.This finally makes exhaust passage 11 on camshaft 15, rolls and turns
The high-pressure exhaust 2 (low pressure exhaust mouth 18) on high pressure gas hole 8 (low pressure exhaust hole 17) and cylinder drive end bearing bracket 1 on son 14
Relative position regular continuous variation in a rotation period of camshaft 15.
In attached drawing 2, B represents the point on the end face of rolling-rotor 14, and A is represented on 15 eccentric part end face of camshaft
Point, they contact with each other.B point, which is limited to, to be moved on radial keyway 16；A point is rotated with camshaft 15, its position
It is not always held on radial keyway 16, that is, A, B point can be separated with the rotation of camshaft 15, represent rolling-rotor
14 and camshaft 15 generate sliding, i.e., described rolling-rotor 14 can be generated when camshaft 15 rotates relative to inclined
The relative rotation around 15 eccentric part axle center of camshaft of heart wheel shaft 15.
Attached drawing 3 is cylinder drive end bearing bracket medial surface schematic diagram.The medial surface of cylinder drive end bearing bracket 1 is provided with radial keyway 16,
Radial keyway 16 is used to the movement of rolling-rotor 14 being limited in single line, and rolling-rotor 14 is forced to rotate in camshaft 15
When, the relative rotation around 15 eccentric part axle center of camshaft relative to camshaft 15 is generated, so that in camshaft
In 15 swing circle, the high pressure gas hole 8 (low pressure exhaust hole 17) on rolling-rotor 14 and the row on camshaft 15
The periodically connection and disconnection of gas channel 11.
Distance R of the inner terminal of radial keyway 16 to 1 center of circle of cylinder drive end bearing bracket2Less than 15 eccentric part cylinder of camshaft
On point to rotation the center of circle shortest distance L1(see Fig. 5), i.e. R2< L1, the outermost end of radial keyway 16 to the circle of cylinder drive end bearing bracket 1
The distance R of the heart3Equal to the inside radius of cylinder block 10, that is to say, that the length of radial keyway 16 will ensure that rolling-rotor 14 can be in gas
It rotates a circle in cylinder.When 14 external cylindrical surface of rolling-rotor is parallel with radial keyway 16 with the normal at 10 inner cavity cylinder point of contact of cylinder block
When, if the point of contact, far from radial keyway 16, cylindrical keys 13 move to the inward flange of radial 16 groove body of keyway；If the point of contact is leaned on
Nearly radial direction keyway 16, then cylindrical keys 13 move to the outer edge of radial 16 groove body of keyway.
The folder of straight line o where 16 groove body of line n and radial keyway at 2 center of circle of high-pressure exhaust and 1 center of cylinder drive end bearing bracket
Straight line o where 16 groove body of the line m at angle θ=135 °, 18 center of circle of low pressure exhaust mouth and 1 center of cylinder drive end bearing bracket and radial keyway
Angle ω=50 °.
The minimum range at the circle of high-pressure exhaust 2 upper and on the circle of low pressure exhaust mouth 18 point to 1 center of cylinder drive end bearing bracket is equal,
It is R1, and the inner arc radius R with the outlet of exhaust passage 11 arc deep gouge5(see Fig. 5) is equal, i.e. R1=R5, to guarantee
In 15 rotation process of camshaft, the company of exhaust passage 11 outlet and high-pressure exhaust 2, low pressure exhaust mouth 18 can be realized respectively
It is logical.
High-pressure exhaust 2 is equal with the maximum distance at point to 1 center of cylinder drive end bearing bracket on the circle of low pressure exhaust mouth 18, is
R4, and the point being less than on camshaft eccentric part cylinder to the rotation center of circle the shortest distance and rolling-rotor wall thickness and, i.e. R4
<1+ δ (see Fig. 5, Fig. 7), to guarantee without exhaust passage 11,10 inner cavity of cylinder block and high-pressure exhaust 2,
Low pressure exhaust mouth 18 will not be connected to.
Attached drawing 4 is camshaft schematic diagram.Exhaust passage 11 is equipped on camshaft 15, exhaust passage 11 is connected to bias
The cylinder of the eccentric part of wheel shaft 15 and an end face.The entrance of exhaust passage 11 is the eccentric part positioned at camshaft 15
Strip arc deep gouge on cylinder, the outlet of exhaust passage 11 be on the end face of the eccentric part of camshaft 15 with turn
The concentric strip arc deep gouge of axis.The inlet and outlet of exhaust passage 11, which are set as strip, to allow compressor to have time enough to be arranged
Gas.
Attached drawing 5 is the end view of camshaft.Camshaft 15 is rotated into the center of circle and 15 eccentric part column of camshaft
The wire definition for rotating the farthest point in the center of circle from camshaft 15 on face is benchmark line q；Exhaust passage 11 exports arc deep gouge edge
The stop and camshaft 15 of rotation direction rotate angle γ=40 ° of line h and reference line q that the center of circle is formed, exhaust passage
11 outlet arc deep gouges rotate the folder of line i and reference line q that the center of circle is formed along the stop and camshaft 15 of rotation opposite direction
Angle α=20 °；The stop of 11 entrance arc deep gouge of exhaust passage in rotational direction and camshaft 15 rotate the line that the center of circle is formed
Angle β=35 ° of k and reference line q.
Attached drawing 6 is the elevational view of camshaft, and Fig. 7 is the elevational view of rolling-rotor.8 center of circle of high pressure gas hole is to gas
Distance and 17 center of circle of low pressure exhaust hole being equidistant to cylinder rear end cap of cylinder rear end cap, are L2, and it is equal to exhaust passage
Distance L of the center line of 11 entrance arc deep gouges to cylinder rear end cap 93, i.e. L2=L3, to guarantee that camshaft 15 was rotating
Cheng Zhong can realize that 11 entrance of exhaust passage and high pressure gas hole 8, low pressure exhaust hole 17 are connected to respectively.
Attached drawing 8 is the end view of rolling-rotor.13 center of circle of cylindrical keys and 14 center of circle of rolling-rotor are formed by line j
Angle Ψ=165 ° of the line f formed with 8 center of circle of high pressure gas hole and 14 center of circle of rolling-rotor；13 center of circle of cylindrical keys and rolling
14 centers of circle of turn are formed by the angle η for the line e that line j and 17 center of circle of low pressure exhaust hole and 14 center of circle of rolling-rotor are formed
=12 °.
Fig. 9 is air-breathing and low pressure compression process schematic diagram.When rolling-rotor 14 crosses air entry 4, a duty cycle
Start, compressor starts carry out compression and new round air-breathing.This event exhaust channel 11 and (the low pressure exhaust hole of high pressure gas hole 8
17), high-pressure exhaust 2 (low pressure exhaust mouth 18) is not attached to lead to, and suction chamber 3 is constantly increased by volume carries out air-breathing, compression chamber 7
Constantly reduced by volume and is compressed.
Figure 10 is that exhaust passage starts to be connected to schematic diagram with low pressure exhaust mouth.As air-breathing and low pressure compression process are further
It carries out, exhaust passage 11 is connected to low pressure exhaust mouth 18 first.Low pressure exhaust hole 17, exhaust passage 11 and low pressure exhaust mouth at this time
18 are not interconnected also.But due to the high pressure gas for remaining a duty cycle in sub-fraction in exhaust passage, thus herein
The discharge of low pressure exhaust mouth 18 can be first passed through by carving remaining gas in exhaust passage 11.
Figure 11 is air-breathing and low pressure exhaust process schematic.When low pressure compression ends, low pressure exhaust hole 17, exhaust passage
11, low pressure exhaust mouth 18 starts to be connected to, and low pressure exhaust formally starts.During this, suction chamber 3 further increases carry out air-breathing.
Figure 12 is that low pressure exhaust terminates schematic diagram.At the end of low pressure exhaust, low pressure exhaust hole 17, exhaust passage 11, low pressure
Exhaust outlet 18 is no longer interconnected.
Figure 13 is air-breathing and high pressure compressed process schematic.After low pressure exhaust, and then compressor carries out high pressure
Compression.This event exhaust channel 11 and high pressure gas hole 8 (low pressure exhaust hole 17), high-pressure exhaust 2 (low pressure exhaust mouth 18) are no
It is connected, suction chamber 3 continues air-breathing, and compression chamber 7 is constantly reduced by volume, further compressed gas.
Figure 14 is air-breathing and high pressure gas process schematic.High pressure compressed end after, high pressure gas hole 8, exhaust passage 11,
High-pressure exhaust 2 starts to be connected to, and high pressure gas starts.During this, suction chamber 3 further increases carry out air-breathing.
Figure 15 is that high pressure gas terminates schematic diagram.Compressor is rotating supreme pressure stomata 8, exhaust passage 11 and high pressure
After port 2 is no longer interconnected, exhaust terminates.When rolling-rotor 14 further crosses air entry 4, air-breathing terminates, compressor
Into the subsequent work period.
By description and accompanying drawings, the exemplary embodiments of the specific structure of specific embodiment are given, based on present invention essence
Mind can also make other conversions, although foregoing invention proposes existing preferred embodiment, however, these contents are not intended as
Limitation.
For a person skilled in the art, after reading above description, various changes and modifications undoubtedly be will be evident.
Therefore, appended claims should regard the whole variations and modifications for covering true intention and range of the invention as.It is weighing
The range and content of any and all equivalences, are all considered as still belonging to the intent and scope of the invention within the scope of sharp claim.
Claims (11)
1. a kind of rolling rotor compressor of double atmospheric pressure, including cylinder block, rolling-rotor, camshaft, air entry, bullet
Spring, slide plate, cylinder drive end bearing bracket, cylinder rear end cap, it is characterised in that: the cylindrical surface of the rolling-rotor is equipped with high pressure gas
Hole and low pressure exhaust hole, the end face of rolling-rotor are embedded with cylindrical keys, and the eccentric part of the camshaft is equipped with connection column
The exhaust passage in face and an end face, the cylinder drive end bearing bracket are equipped with high-pressure exhaust and low pressure exhaust mouth, cylinder front end
Lid medial surface is equipped with radial keyway, and the cylindrical keys are inserted into radial keyway.
2. a kind of rolling rotor compressor of double atmospheric pressure according to claim 1, it is characterised in that: the circle
The equivalent width of the diameter of cylindricality key and radial keyway.
3. a kind of rolling rotor compressor of double atmospheric pressure according to claim 2, it is characterised in that: radial keyway
Inner terminal to the cylinder drive end bearing bracket center of circle distance be less than camshaft eccentric part cylinder on point to rotate the center of circle it is most short
Distance, the outermost end of radial keyway are equal to the inside radius of cylinder block to the distance in the cylinder drive end bearing bracket center of circle.
4. a kind of rolling rotor compressor of double atmospheric pressure according to claim 3, it is characterised in that: turn when rolling
When sub- external cylindrical surface and the normal at cylinder intracoelomic cavity cylinder point of contact parallel with radial keyway, if the separate radial keyway in the point of contact,
Cylindrical keys move to the inward flange of radial keyway groove body；If the point of contact moves to radial direction close to radial keyway, cylindrical keys
The outer edge of keyway groove body.
5. a kind of rolling rotor compressor of double atmospheric pressure according to claim 1, it is characterised in that: the row
The outlet in gas channel is the strip arc deep gouge concentric with shaft on an end face of camshaft eccentric part, described
The entrance of exhaust passage be strip arc deep gouge on the cylinder of camshaft eccentric part.
6. a kind of rolling rotor compressor of double atmospheric pressure according to claim 5, it is characterised in that: by eccentric wheel
Axis rotates on the basis of the wire definition of point farthest from the camshaft rotation center of circle on the center of circle and camshaft eccentric part cylinder
Line；The line and reference line of the stop of Vent passageway arc deep gouge in rotational direction and camshaft rotation center of circle formation
Angle is 40 °, the line that Vent passageway arc deep gouge is formed along the stop of rotation opposite direction and the camshaft rotation center of circle
Angle with reference line is 20 °；The stop of exhaust passage entrance arc deep gouge in rotational direction and camshaft rotate center of circle shape
At line and the angle of reference line be 35 °.
7. a kind of rolling rotor compressor of double atmospheric pressure according to claim 6, it is characterised in that: high pressure gas
The hole center of circle to cylinder rear end cap distance and the low pressure exhaust hole center of circle being equidistant to cylinder rear end cap, and be equal to exhaust passage
Distance of the center line of entrance arc deep gouge to cylinder rear end cap.
8. a kind of rolling rotor compressor of double atmospheric pressure according to claim 1, it is characterised in that: the height
The angle of straight line is 135~165 ° where the line and radial keyway groove body at the pressure port center of circle and cylinder drive end bearing bracket center, low
The angle of straight line is 20~50 ° where the line and radial keyway groove body at the pressure port center of circle and cylinder drive end bearing bracket center, high pressure
The minimum range at exhaust outlet circle upper and on low pressure exhaust mouth circle point to cylinder drive end bearing bracket center is equal, and goes out equal to exhaust passage
The inner arc radius of mouthful arc deep gouge, the maximum of point on high-pressure exhaust and low pressure exhaust mouth circle to cylinder drive end bearing bracket center
The shortest distance and rolling-rotor wall thickness of the point for being equidistant, and being less than on camshaft eccentric part cylinder to the rotation center of circle
With.
9. a kind of rolling rotor compressor of double atmospheric pressure according to claim 2, it is characterised in that: cylindrical keys
The line angle that the center of circle and the rolling-rotor center of circle are formed by line and the high pressure gas hole center of circle is formed with the rolling-rotor center of circle is
160~190 °；The cylindrical keys center of circle and the rolling-rotor center of circle are formed by line and the low pressure exhaust hole center of circle and rolling-rotor circle
The line angle being formed centrally is 0~20 °.
10. according to claim 1 to a kind of rolling rotor compressor of double atmospheric pressure described in 9 any claims,
Be characterized in that: for cylinder block by cylinder drive end bearing bracket side embedded with positioning pin, cylinder drive end bearing bracket medial surface is equipped with location hole.
11. the process of the rolling rotor compressor compression exhaust of double atmospheric pressure according to claim 1, feature exist
In: when work, motor driven camshaft is rotated, and the movement of the cylindrical keys on rolling-rotor is because being limited in diameter
Into key keyway, so that rolling-rotor has the relative rotation around camshaft eccentric part axle center, and cylinder drive end bearing bracket is
Static, the relative position for being finally reached exhaust passage, high pressure and low pressure exhaust hole and high pressure and low pressure exhaust mouth turns at one
Regular continuous variation in the dynamic period.In compression process, exhaust passage, high pressure gas hole (low pressure exhaust hole), high-pressure exhaust
(low pressure exhaust mouth) is not attached to lead to, and ensure that the progress of compression；In low pressure exhaust, only exhaust passage, low pressure exhaust hole and low
Pressure port is connected, and ensure that the progress of low pressure exhaust；In high pressure gas, only exhaust passage, high pressure gas hole and high pressure
Exhaust outlet is connected, and ensure that the progress of high pressure gas.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710969318.4A CN109611332B (en) | 2017-10-05 | 2017-10-05 | Double-exhaust-pressure rolling rotor type compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710969318.4A CN109611332B (en) | 2017-10-05 | 2017-10-05 | Double-exhaust-pressure rolling rotor type compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109611332A true CN109611332A (en) | 2019-04-12 |
| CN109611332B CN109611332B (en) | 2023-09-22 |
Family
ID=66001526
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710969318.4A Active CN109611332B (en) | 2017-10-05 | 2017-10-05 | Double-exhaust-pressure rolling rotor type compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN109611332B (en) |
Citations (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS57146088A (en) * | 1981-03-04 | 1982-09-09 | Mitsubishi Heavy Ind Ltd | Rotary compressor |
| JPH05215087A (en) * | 1992-02-05 | 1993-08-24 | Shingo Saida | Rotary compressor |
| JPH08193584A (en) * | 1995-01-13 | 1996-07-30 | Toshiba Corp | Rotary type compressor |
| JPH10131878A (en) * | 1996-10-28 | 1998-05-19 | Zexel Corp | Vane type compressor |
| JPH11351173A (en) * | 1998-06-05 | 1999-12-21 | Zexel:Kk | Vane type compressor |
| KR20040007004A (en) * | 2002-07-16 | 2004-01-24 | 삼성전자주식회사 | Rotary compprersor |
| JP2008038697A (en) * | 2006-08-03 | 2008-02-21 | Mitsubishi Electric Corp | Multiple stage rotary compressor |
| CN201269198Y (en) * | 2008-09-04 | 2009-07-08 | 上海日立电器有限公司 | Exhaustion structure used for compressor |
| US20110058970A1 (en) * | 2009-09-10 | 2011-03-10 | Jason James Hugenroth | Rotary compressor and method |
| WO2013172144A1 (en) * | 2012-05-18 | 2013-11-21 | カルソニックカンセイ株式会社 | Gas compressor |
| CN203730328U (en) * | 2013-12-26 | 2014-07-23 | 瑞智(青岛)精密机电有限公司 | Rotary type air conditioning compressor |
| CN105201835A (en) * | 2015-10-19 | 2015-12-30 | 广西大学 | Swing rotor compressor |
| CN106968947A (en) * | 2016-11-10 | 2017-07-21 | 桂林航天工业学院 | Swinging rotor type compressor |
| CN107120280A (en) * | 2017-07-12 | 2017-09-01 | 张均 | Compression set and compressor |
| CN207920856U (en) * | 2017-10-05 | 2018-09-28 | 桂林航天工业学院 | A kind of rolling rotor compressor of double atmospheric pressure |
-
2017
- 2017-10-05 CN CN201710969318.4A patent/CN109611332B/en active Active
Patent Citations (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS57146088A (en) * | 1981-03-04 | 1982-09-09 | Mitsubishi Heavy Ind Ltd | Rotary compressor |
| JPH05215087A (en) * | 1992-02-05 | 1993-08-24 | Shingo Saida | Rotary compressor |
| JPH08193584A (en) * | 1995-01-13 | 1996-07-30 | Toshiba Corp | Rotary type compressor |
| JPH10131878A (en) * | 1996-10-28 | 1998-05-19 | Zexel Corp | Vane type compressor |
| JPH11351173A (en) * | 1998-06-05 | 1999-12-21 | Zexel:Kk | Vane type compressor |
| KR20040007004A (en) * | 2002-07-16 | 2004-01-24 | 삼성전자주식회사 | Rotary compprersor |
| JP2008038697A (en) * | 2006-08-03 | 2008-02-21 | Mitsubishi Electric Corp | Multiple stage rotary compressor |
| CN201269198Y (en) * | 2008-09-04 | 2009-07-08 | 上海日立电器有限公司 | Exhaustion structure used for compressor |
| US20110058970A1 (en) * | 2009-09-10 | 2011-03-10 | Jason James Hugenroth | Rotary compressor and method |
| WO2013172144A1 (en) * | 2012-05-18 | 2013-11-21 | カルソニックカンセイ株式会社 | Gas compressor |
| CN104302923A (en) * | 2012-05-18 | 2015-01-21 | 卡森尼可关精株式会社 | Gas compressor |
| CN203730328U (en) * | 2013-12-26 | 2014-07-23 | 瑞智(青岛)精密机电有限公司 | Rotary type air conditioning compressor |
| CN105201835A (en) * | 2015-10-19 | 2015-12-30 | 广西大学 | Swing rotor compressor |
| CN106968947A (en) * | 2016-11-10 | 2017-07-21 | 桂林航天工业学院 | Swinging rotor type compressor |
| CN107120280A (en) * | 2017-07-12 | 2017-09-01 | 张均 | Compression set and compressor |
| CN207920856U (en) * | 2017-10-05 | 2018-09-28 | 桂林航天工业学院 | A kind of rolling rotor compressor of double atmospheric pressure |
Also Published As
| Publication number | Publication date |
|---|---|
| CN109611332B (en) | 2023-09-22 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| EP2251545B1 (en) | A rotary compressor | |
| CN207920856U (en) | A kind of rolling rotor compressor of double atmospheric pressure | |
| CN106968947B (en) | Swinging rotor type compressor | |
| CN105179020B (en) | Expansion machinery suction control device | |
| CN204025047U (en) | A kind of multi-stage roots vacuum pump | |
| CN105201835B (en) | A kind of swing-rotor compressor | |
| CN207920873U (en) | A kind of rolling rotor compressor | |
| CN206234110U (en) | A kind of transfiguration water pump of the formula rotor that dangled based on triangle | |
| CN207920858U (en) | A kind of double atmospheric pressure compressor with rolling rotor | |
| WO2018033080A1 (en) | Rotary engine and power output method | |
| CN109611337A (en) | A kind of rolling rotor compressor | |
| CN109611332A (en) | A kind of rolling rotor compressor of double atmospheric pressure | |
| CN203847388U (en) | Rotary vane vacuum pump | |
| CN103821715B (en) | Translation revolving compressor mechanical | |
| CN109611334A (en) | A kind of double atmospheric pressure compressor with rolling rotor | |
| CN206329495U (en) | Swinging rotor type compressor | |
| CN104141532B (en) | Rolling valve rolling-rotor engine | |
| CN104564678B (en) | Expansion compressor device and the air-conditioner with it | |
| CN201193614Y (en) | Air inlet mechanism of rotary compressor cylinder | |
| CN103867440A (en) | Compressor | |
| CN207437347U (en) | Rotating boosting pumps | |
| CN207920874U (en) | A kind of rolling rotor compressor | |
| CN203114626U (en) | Rotary compressor with slide groove balance hole | |
| CN207728566U (en) | A kind of self-enclosed slide vane compressor of low speed | |
| CN202280620U (en) | Rotary compressor with enhanced vapor injection function |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |