CN106438359B - The operation method of compressor, heat exchange equipment and compressor - Google Patents
The operation method of compressor, heat exchange equipment and compressor Download PDFInfo
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- CN106438359B CN106438359B CN201510482483.8A CN201510482483A CN106438359B CN 106438359 B CN106438359 B CN 106438359B CN 201510482483 A CN201510482483 A CN 201510482483A CN 106438359 B CN106438359 B CN 106438359B
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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
- F04C18/30—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
- F04C18/34—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 the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
Abstract
The present invention provides the operation methods of a kind of compressor, heat exchange equipment and compressor.Compressor includes: upper flange；Lower flange；At least two cylinders, at least two cylinders are folded between upper flange and lower flange, and two cylinders of arbitrary neighborhood are interconnected so that compressor forms compound compressor；Rotating assembly, rotating assembly sequentially passes through upper flange, cylinder and lower flange, rotating assembly includes the sub- shaft being arranged in a one-to-one correspondence with each cylinder at least two cylinders, and the axle center eccentric setting and eccentric distance of the axle center of sub- shaft cylinder corresponding with the sub- shaft are fixed；Piston component, piston component has to be pivotally disposed in cylinder with the one-to-one capacity chamber of each cylinder, piston component, and at least one sub- shaft and piston component are drivingly connected to change the volume of capacity chamber.Vibration can be effectively relieved in compressor in the present invention, and guarantees that the volume variation of capacity chamber has rule, reduces clearance volume, improve the operation stability of compressor.
Description
Technical field
The present invention relates to heat-exchange system technical fields, in particular to a kind of compressor, heat exchange equipment and compressor
Operation method.
Background technique
Compressor in the prior art includes compressor and expanding machine etc..By taking compressor as an example.
During the motion, the position of the mass center of the two is the sub- shaft and cylinder of piston compressor in the prior art
Variation.Motor driven crankshafts output power is moved back and forth in cylinder by crankshaft driving piston and is done come compressed gas or liquid
Function, to achieve the purpose that compressed gas or liquid.
There are many defects for traditional piston compressor: due to the presence of suction valve chip and exhaust valve plate, causing to inhale, arrange
Atmidometer increases, while increasing suction and discharge noise；Lateral force suffered by the cylinder of compressor is larger, and lateral force flogs a dead horse, drop
Low compressor efficiency；Crankshaft drives reciprocating motion of the pistons, and eccentric mass is larger, causes vibration of compressor big；Compressor passes through song
Handle link mechanism drives one or more pistons works, and structure is complicated；The lateral force that crankshaft and piston are subject to is larger, and piston is easy
Abrasion, causes piston seal performance to reduce.And existing compressor leaks the reasons such as big, volumetric efficiency since there are clearance volumes
It is low, and be difficult to further increase.
Moreover, the mass center of the eccentric part in piston compressor, which moves in a circle, generates that a size is constant, direction
The centrifugal force of change, the centrifugal force cause vibration of compressor to aggravate.
Summary of the invention
The main purpose of the present invention is to provide the operation methods of a kind of compressor, heat exchange equipment and compressor, to solve
Compressor in the prior art has that movement is unstable, vibration is big, there are clearance volumes.
To achieve the goals above, according to an aspect of the invention, there is provided a kind of compressor, comprising: upper flange；Under
Flange；At least two cylinders, at least two cylinders are folded between upper flange and lower flange, and two cylinders of arbitrary neighborhood mutually interconnect
Passing to makes compressor form compound compressor；Rotating assembly, rotating assembly sequentially pass through upper flange, cylinder and lower flange, shaft
Component includes the sub- shaft being arranged in a one-to-one correspondence with each cylinder at least two cylinders, the axle center of sub- shaft and the sub- shaft
The axle center eccentric setting and eccentric distance of corresponding cylinder are fixed；Piston component, piston component have a pair of with each cylinder one
The capacity chamber answered, piston component are pivotally disposed in cylinder, and at least one sub- shaft and piston component are drivingly connected
To change the volume of capacity chamber.
Further, piston component includes: piston bush, and piston bush is pivotally disposed in cylinder；At least two pistons,
Piston is slidably arranged in piston bush to form capacity chamber, and capacity chamber is located in the glide direction of piston.
Further, cylinder, sub- shaft, piston are respectively two, and a sub- shaft is driving shaft, protrude into and lean on across upper flange
In the cylinder of nearly upper flange side, and it is connect with the piston motion in the cylinder；Another sub- shaft is driven axle, passes through laxative remedy
Orchid protrudes into the cylinder of lower flange side, and connect with the piston motion in the cylinder.
Further, rotation is driven by motor in driving shaft, and driven axle is driven rotation by driving shaft indirectly.
Further, piston has the slip hole axially through setting along sub- shaft, and sub- shaft passes through slip hole, with master
The piston of moving axis cooperation is under the driving of driving shaft with spindle rotation and simultaneously along the axis direction perpendicular to driving shaft in work
It reciprocatingly slides in plug sleeve；With the piston of driven axle cooperation, is rotated under the driving of piston bush with piston bush and driven axle is driven to revolve
Turn, while reciprocatingly sliding in piston bush with the piston of driven axle cooperation along the axis direction perpendicular to driven axle.
Further, slip hole is long hole or kidney slot.
Further, piston has symmetrically arranged a pair of of the curved surfaces of middle vertical plane along piston, curved surfaces and cylinder
Inner surface adaptability cooperation, and two times of the cambered surface radius of curvature of curved surfaces be equal to cylinder internal diameter.
Further, piston is cylindrical.
Further, the pilot hole with the radial perforation setting along piston bush in piston bush, pilot hole at least two,
A piston is correspondingly arranged in each pilot hole, piston is slidably arranged in pilot hole with linear reciprocating motion.
Further, the axis of each pilot hole is parallel.
Further, partition is formed between pilot hole two neighboring in piston bush, is offered on partition for being connected to phase
The oil-through hole of adjacent two pilot holes.
Further, the axis of oil-through hole is parallel with the axis of sub- shaft.
Further, orthographic projection of the pilot hole at lower flange has a pair of parallel straightway, a pair of parallel
Straightway is that the parallel inner wall of a pair of piston bush projects to be formed, and piston has the inner wall parallel with a pair of pilot hole
Face shape is adapted and slides the outer mold surface of cooperation.
Further, the first thrust surface towards lower flange side of piston bush is contacted with the surface of lower flange.
Further, sub- shaft has the sliding section being slidably matched with piston component, and sliding section is located at the close of sub- shaft
One end of cylinder, and section is slid with sliding mating surface.
Further, sliding mating surface is symmetricly set on the two sides of sliding section.
Further, sliding mating surface is parallel with the axial plane of sub- shaft, slides the slip hole of mating surface and piston
Inner wall be slidably matched in the axis direction perpendicular to sub- shaft.
Further, compressor further includes the intermediate flow channel being arranged on cylinder, and two neighboring cylinder passes through intermediate flow channel
Connection.
Further, the cylinder wall of the low-pressure stage cylinder at least two cylinders has air inlet and communication port, communication port
It is connected to by the intermediate flow channel on low-pressure stage cylinder with the intermediate flow channel of the hiigh pressure stage cylinder at least two cylinders.
Further, the inner wall of the cylinder wall of low-pressure stage cylinder has low-pressure stage air inlet dashpot, and low-pressure stage air inlet is slow
Jet-bedding is connected to air inlet.
Further, low-pressure stage air inlet dashpot is arc-shaped section in the sagittal plane of low-pressure stage cylinder, and low pressure is grading
The both ends of gas dashpot are extended from air inlet to communication port position.
Further, the outside wall surface of the cylinder wall of low-pressure stage cylinder has connectivity slot, and communication port is connected to connectivity slot, compresses
Machine further includes sealing plate, and sealing plate is arranged in close connectivity slot at the notch of connectivity slot, and connectivity slot and communication port form low-pressure stage
The intermediate flow channel of cylinder.
Further, the inner wall of the cylinder wall of hiigh pressure stage cylinder has hiigh pressure stage air inlet dashpot and exhaust outlet, high pressure
Grade air inlet dashpot is connected to the intermediate flow channel of hiigh pressure stage cylinder, and exhaust outlet is connected to the cavity of compressor.
Further, hiigh pressure stage cylinder also has gas supplementing opening, and gas supplementing opening is connected to hiigh pressure stage air inlet dashpot.
Further, hiigh pressure stage air inlet dashpot is arc-shaped section in the sagittal plane of hiigh pressure stage cylinder, and high pressure is grading
The both ends of gas dashpot are extended from gas supplementing opening to exhaust outlet position.
Further, sub- shaft has an oil leab, oil leab include be arranged in internal galleries inside sub- shaft and
The oil-through-hole of external oil duct at sliding mating surface and connection internal galleries and external oil duct is set.
Further, the heart is arranged two neighboring cylinder coaxially to each other.
Further, the axle center eccentric setting in the axle center of upper flange and the cylinder close to the setting of upper flange side.
Further, the axle center eccentric setting in the axle center of lower flange and the cylinder close to the setting of lower flange side.
Further, compressor further includes support plate, and support plate is arranged on the end face of separate cylinder side of lower flange,
And support plate and the concentric setting of lower flange, to support rotating assembly, support plate has the second thrust for being used to support rotating assembly
Face.
Further, compressor further includes at least two exhaust valve components, and communication port and exhaust ports correspond to each setting
There is an exhaust valve component.
Further, holding tank is offered on the outer wall of the cylinder wall of hiigh pressure stage cylinder, exhaust outlet penetrates through the slot of holding tank
Bottom, an exhaust valve component are arranged in holding tank.
Further, each exhaust valve component includes: exhaust valve plate, and exhaust valve plate blocks communication port or exhaust outlet；Valve
Piece baffle, valve block baffle are stacked on exhaust valve plate.
According to another aspect of the present invention, a kind of heat exchange equipment, including compressor are provided, compressor is above-mentioned compression
Machine.
Further, heat exchange equipment further includes First Heat Exchanger, the second heat exchanger and four-way valve, compressor, the first heat exchange
Device and the second heat exchanger pass through four-way valve formation circulating heat exchanging pipe, heat exchange equipment further include: flash vessel, flash vessel setting are following
On ring heat exchanging pipe and between First Heat Exchanger and the second heat exchanger；Gas tonifying branch, the first end and flash distillation of gas tonifying branch
Device connection, the gas supplementing opening of the hiigh pressure stage cylinder of the second end and compressor of gas tonifying branch are connected to.
According to another aspect of the present invention, a kind of operation method of compressor is provided, comprising: sub- shaft is around sub- shaft
Axle center O1Rotation；Axle center O of the piston bush around cylinder2Rotation, and the axle center eccentric setting and eccentricity in the axle center of sub- shaft and cylinder
From fixation；The piston of piston component is under the driving of sub- shaft with the rotation of sub- shaft and simultaneously along the axis side perpendicular to sub- shaft
It reciprocatingly slides in the piston bush of piston component.
Further, operation method uses cross slides principle, wherein piston is as sliding block, the sliding of sub- shaft
Mating surface is as first connecting rod l1, piston bush pilot hole as second connecting rod l2。
It applies the technical scheme of the present invention, is interconnected between two cylinders of arbitrary neighborhood so that compressor forms multistage pressure
Contracting machine, by by the axle center eccentric setting of the axle center of the sub- shaft in rotating assembly cylinder corresponding with the sub- shaft and will be eccentric
Distance is fixed, thus rotate sub- shaft and cylinder around respective axle center during the motion, and centroid position is constant, so that
Piston component can be stablized and continuously rotate in cylinder motion, and the vibration of compressor has been effectively relieved, and guarantee transfiguration
The volume variation of product chamber has rule, reduces clearance volume, to improve the operation stability of compressor, and then improves
The functional reliability of heat exchange equipment.
Detailed description of the invention
The accompanying drawings constituting a part of this application is used to provide further understanding of the present invention, and of the invention shows
Examples and descriptions thereof are used to explain the present invention for meaning property, does not constitute improper limitations of the present invention.In the accompanying drawings:
Fig. 1 shows the structural schematic diagram of the compressor in the present invention；
Fig. 2 shows the explosive views of the pump assembly in the present invention；
Fig. 3 show sub- shaft in the present invention, upper flange, cylinder and lower flange installation relation schematic diagram；
Fig. 4 shows the schematic diagram of internal structure of Fig. 3；
Fig. 5 shows the installation relation schematic diagram of piston bush in the present invention, piston and sub- shaft；
Fig. 6 shows the installation relation schematic diagram of upper flange in the present invention, piston bush, piston and sub- shaft；
Fig. 7 shows the structural schematic diagram of the sub- shaft of the close upper flange side in the present invention；
Fig. 8 shows the schematic diagram of internal structure of the sub- shaft in Fig. 7；
Fig. 9 shows the structural schematic diagram of the sub- shaft of the close lower flange side in the present invention；
Figure 10 a shows the schematic diagram of internal structure of the sub- shaft in Fig. 9；
Figure 10 b shows the top view of the sub- shaft in Fig. 9；
Figure 11 shows the structural schematic diagram of the piston in the present invention；
Figure 12 shows the structural schematic diagram of another angle of the piston in Figure 11；
Figure 13 shows the structural schematic diagram of the support plate in the present invention；
Figure 14 shows the structural schematic diagram of the piston bush in the present invention；
Figure 15 shows the cross-sectional view of the piston bush in the present invention；
Figure 16 shows the structural schematic diagram of the upper flange in the present invention；
Figure 17 shows the structural schematic diagrams of the lower flange in the present invention；
Figure 18 shows the axle center and piston bush axle center of the sub- shaft of the close lower flange side at the lower flange of Figure 17
Eccentric relationship schematic diagram；
Figure 19 shows the structural schematic diagram of the hiigh pressure stage cylinder in the present invention；
Figure 20 shows the cross-sectional view of the hiigh pressure stage cylinder in Figure 19；
Figure 21 shows the assembly relation schematic diagram of hiigh pressure stage cylinder in the present invention, sub- shaft, piston bush and piston；
Figure 22 shows the structural schematic diagram of the low-pressure stage cylinder in the present invention；
Figure 23 shows the cross-sectional view of the low-pressure stage cylinder in Figure 22；
Figure 24 shows the cross-sectional view of another angle of the low-pressure stage cylinder in Figure 22；
Figure 25 shows the assembly relation schematic diagram of low-pressure stage cylinder in the present invention, sub- shaft, piston bush and piston；
Figure 26 shows the assembly relation schematic diagram of low-pressure stage cylinder and hiigh pressure stage cylinder in the present invention；
Figure 27 shows the explosive view of Figure 26；
Figure 28 shows the cross-sectional view of an angle in Figure 26；
Figure 29 shows the working state schematic representation when piston in the present invention is in preparation beginning air-breathing；
Figure 30 shows the working state schematic representation that the piston in the present invention is in breathing process；
Figure 31 show the piston in the present invention be in air-breathing complete and start compression when working state schematic representation；
Figure 32 shows the working state schematic representation when piston in the present invention is in gas compression and is vented；
Figure 33 shows the working state schematic representation when piston in the present invention is in exhaust completion；
Figure 34 shows the structural schematic diagram of the heat exchange equipment in the present invention；
Figure 35 shows the working state schematic representation of the piston in the hiigh pressure stage cylinder in the present invention；
Figure 36 shows the working principle diagram of the compressor in the present invention.
Wherein, the above drawings include the following reference numerals:
10, sub- shaft；11, section is slid；111, mating surface is slid；13, oil leab；14, oil-through-hole；15, close to laxative remedy
The axle center of the sub- shaft of blue side；20, low-pressure stage cylinder；21, air inlet；22, exhaust outlet；23, hiigh pressure stage air inlet dashpot；
24, communication port；25, holding tank；26, intermediate flow channel；27, gas supplementing opening；28, connectivity slot；29, low-pressure stage air inlet dashpot；200,
Hiigh pressure stage cylinder；31, capacity chamber；311, pilot hole；32, piston；321, slip hole；33, piston bush；332, the first thrust
Face；333, piston bush axle center；34, partition；35, oil-through hole；40, exhaust valve component；41, exhaust valve plate；42, valve block baffle；43,
First fastener；50, upper flange；60, lower flange；61, support plate；611, the second thrust surface；70, the second fastener；80, third
Fastener；81, sealing plate；82, the 5th fastener；83, the 4th fastener；84, first throttle element；85, the second restricting element；
86, shut-off valve；87, increasing enthalpy component；322, piston centroid trajectory line；90, dispenser component；91, housing unit；92, motor group
Part；93, pump assembly；94, cover assembly；95, lower cover and mounting plate；96, First Heat Exchanger；97, the second heat exchanger；98, four
Port valve；99, flash vessel.
Specific embodiment
It should be noted that in the absence of conflict, the features in the embodiments and the embodiments of the present application can phase
Mutually combination.The present invention will be described in detail below with reference to the accompanying drawings and embodiments.
It is noted that following detailed description is all illustrative, it is intended to provide further instruction to the application.Unless another
It indicates, all technical and scientific terms used herein has usual with the application person of an ordinary skill in the technical field
The identical meanings of understanding.
In the present invention, in the absence of explanation to the contrary, the noun of locality used is usually directed to attached drawing as " left and right "
Shown in it is left and right；" inside and outside " refers to the inside and outside of the profile relative to each component itself, but the above-mentioned noun of locality is not limited to
The present invention.
In order to solve the problems, such as that compressor in the prior art is unstable in the presence of movement, vibration is big, there are clearance volume, this hairs
It is bright to provide a kind of compressor and heat exchange equipment, wherein heat exchange equipment includes following compressor.In addition, additionally providing one kind
The operation method of compressor.
As shown in Fig. 2 to Figure 33, compressor includes upper flange 50, lower flange 60, at least two cylinders, rotating assembly and work
Plug assembly, at least two cylinders are folded between upper flange 50 and lower flange 60, two cylinders of arbitrary neighborhood be interconnected so that
Compressor forms compound compressor, and rotating assembly sequentially passes through upper flange 50, cylinder and lower flange 60, rotating assembly include with extremely
The sub- shaft 10 that each cylinder in few two cylinders is arranged in a one-to-one correspondence, the axle center of sub- shaft 10 are corresponding with the sub- shaft 10
The axle center eccentric setting and eccentric distance of cylinder are fixed, piston component have with the one-to-one capacity chamber 31 of each cylinder,
Piston component is pivotally disposed in cylinder, and at least one sub- shaft 10 is drivingly connected with piston component to change capacity
The volume of chamber 31.Wherein, upper flange 50 is fixed by the second fastener 70 and the cylinder close to 50 side of upper flange, lower flange 60
It is fixed by third fastener 80 and the cylinder close to 60 side of lower flange.
Preferably, the second fastener 70 and/or third fastener 80 are screw or bolt.
Preferably, the first pump housing screw hole worn for the second fastener 70 is provided on upper flange 50.On lower flange 60
The second pump housing screw hole worn there are four being arranged for third fastener 80.
It should be noted that the mass center of the center of the first pump housing screw hole on upper flange 50 and upper flange 50 exists centainly
Eccentric distance e.This eccentricity determines the discharge capacity of the cylinder close to 50 side of upper flange, when cylinder rotates a circle, gas displacement V
=2*2e*S, wherein S is piston main body feature cross-section product.
It is interconnected between two cylinders of arbitrary neighborhood so that compressor forms compound compressor, by will be in rotating assembly
Sub- shaft 10 axle center cylinder corresponding with the sub- shaft 10 axle center eccentric setting and eccentric distance is fixed, to make son
Shaft 10 and cylinder are rotated around respective axle center during the motion, and centroid position is constant, so that piston component is in cylinder
When interior movement, it can stablize and continuously rotate, the vibration of compressor has been effectively relieved, and guarantee that the volume of capacity chamber 31 becomes
Changing has rule, reduces clearance volume, to improve the operation stability of compressor, and then improves the work of heat exchange equipment
Make reliability.
It should be noted that the heart is arranged two neighboring cylinder coaxially to each other.Preferably, the axle center of upper flange 50 with close to upper
The axle center eccentric setting of the cylinder of 50 side of flange setting.Preferably, the axle center of lower flange 60 is set with close to 60 side of lower flange
The axle center eccentric setting for the cylinder set.The cylinder being installed in the above way can guarantee cylinder and sub- shaft 10 or upper flange 50
Eccentricity fix, so that piston component be made to have the characteristics that kinetic stability is good.
Sub- shaft 10 in the present invention is slidably connected with piston component, and the volume of capacity chamber 31 turns with sub- shaft 10
It moves and changes.Since the sub- shaft 10 in the present invention is slidably connected with piston component, hereby it is ensured that the movement of piston component can
By property, piston component is effectively avoided to move stuck problem, so that changing the volume of capacity chamber 31 has the characteristics that rule.
As shown in Fig. 2, Fig. 5 to Fig. 6, Figure 21, Figure 25, piston component includes piston bush 33 and at least two pistons 32, is lived
Plug sleeve 33 is pivotally disposed in cylinder, and piston 32 is slidably arranged in piston bush 33 to form capacity chamber 31, and transfiguration
Product chamber 31 is located in the glide direction of piston 32.Optionally, the number of piston 32 and the number of cylinder are consistent.
In this specific embodiment, piston component is slidably matched with sub- shaft 10, and with the rotation of sub- shaft 10, piston
Component has linear motion trend relative to sub- shaft 10, so that rotation be made to become local linear motion.Due to piston 32 with
Piston bush 33 is slidably connected, thus under the driving of sub- shaft 10, effectively avoid piston 32 from moving stuck, to ensure that piston
32, the motion credibility of sub- shaft 10 and piston bush 33, and then improve the operation stability of compressor.
In the preferred embodiment shown in Fig. 1 to Figure 33, Figure 36, cylinder, sub- shaft 10, piston 32 are respectively two, one
A sub- shaft 10 passes through upper flange 50 as driving shaft and protrudes into the cylinder close to 50 side of upper flange, and with the work in the cylinder
32 movement connection of plug；Another sub- shaft 10 passes through the cylinder that lower flange 60 protrudes into close 60 side of lower flange as driven axle
It is interior, and move and connect with the piston 32 in the cylinder.Due to forming crosshead shoe machine between piston component, cylinder and sub- shaft 10
Structure, thus make the motion stabilization of piston component and cylinder and continuous, and guarantee that the volume variation of capacity chamber 31 has rule, from
And it ensure that the operation stability of compressor, and then improve the functional reliability of heat exchange equipment.
Rotation is driven by motor in driving shaft, and driven axle is driven rotation by driving shaft indirectly.
Piston 32 in the present invention has the slip hole 321 axially through setting along sub- shaft 10, and sub- shaft 10 passes through
Slip hole 321, the piston 32 cooperated with driving shaft is under the driving of driving shaft with spindle rotation and simultaneously along perpendicular to actively
The axis direction of axis reciprocatingly slides in piston bush 33；The piston 32 cooperated with driven axle, with work under the driving of piston bush 33
Plug sleeve 33 rotates and driven axle is driven to rotate, while existing with the piston 32 of driven axle cooperation along the axis direction perpendicular to driven axle
It reciprocatingly slides in piston bush 33.Due to moving in a straight line piston 32 relative to sub- shaft 10 rather than rotary reciprocating motion, thus
Effectively reduce eccentric mass, reduce sub- shaft 10 and lateral force that piston 32 is subject to, thus reduce the abrasion of piston 32,
Improve the sealing performance of piston 32.
For above-mentioned driven axle, that is, for the sub- shaft 10 that is positioned close in the cylinder of 60 side of lower flange,
The rotation of piston bush 33 is simultaneously rotated with piston 32, and the piston 32 close to the setting of 60 side of lower flange can slide in piston bush 33
To change the volume of corresponding capacity chamber 31, while the driving close to the sub- shaft 10 of 60 side of lower flange in the piston 32 is made
Single part is reduced so that piston bush 33 and the sub- shaft 10 be made to be respectively subjected to bending deformation and torsional deflection with lower rotation
Overall deformation, reduce the Structural strength calls to sub- shaft 10.
Preferably, slip hole 321 is long hole or kidney slot.
Piston 32 in the present invention is cylindrical.Preferably, piston 32 is cylindrical or non-cylindrical.
As is illustrated by figs. 11 and 12, piston 32 has symmetrically arranged a pair of of the curved surfaces of middle vertical plane along piston 32, arc
The cooperation of the inner surface adaptability of shape surface and cylinder, and two times of the cambered surface radius of curvature of curved surfaces are equal to the internal diameter of cylinder.
In this way, can make that Zero clearance volume can be achieved in exhaust process.It should be noted that when piston 32 is placed in piston bush 33
When, the middle vertical plane of piston 32 is the axial plane of piston bush 33.
The main structure of piston bush 33 in the present invention is the hollow cylinder for having certain roughness requirement.
There is the radial perforation along piston bush 33 to set in Figure 14 and preferred embodiment shown in figure 15, in piston bush 33
The pilot hole 311 set, pilot hole 311 are at least two, are correspondingly arranged on a piston 32, piston 32 in each pilot hole 311
It is slidably arranged in pilot hole 311 with linear reciprocating motion.Since piston 32 is slidably arranged in pilot hole 311, thus when work
Plug 32 when side-to-side movement, can be such that the volume of capacity chamber 31 constantly changes in pilot hole 311, to guarantee the suction of compressor
Gas, exhaust stability.
Piston 32 rotates in piston bush 33 in order to prevent, and orthographic projection of the pilot hole 311 at lower flange 60 has a pair
Parallel straightway, a pair of parallel straightway are that the parallel inner wall of a pair of piston bush 33 projects to be formed, piston
32 there is the inner wall shape parallel with a pair of pilot hole 311 to be adapted and slide the outer mold surface of cooperation.Such as above structure
The piston 32 and piston bush 33 of cooperation can make piston 32 smooth sliding and holding sealing effect in piston bush 33.
Preferably, orthographic projection of the pilot hole 311 at lower flange 60 has a pair of of arcuate line segment, a pair of arcuate line segment and
A pair of parallel straightway is joined to form irregular cross sectional shape.
As shown in Fig. 2, the outer peripheral surface of piston bush 33 is adapted with the inner wall shape of cylinder.So that piston bush 33 with
It is big face sealing between cylinder, between pilot hole 311 and piston 32, and complete machine sealing is big face sealing, is conducive to reduce and let out
Leakage.
As shown in figure 5, the surface of the first thrust surface 332 and lower flange 60 towards 60 side of lower flange of piston bush 33 connects
Touching.To make piston bush 33 and 60 reliable location of lower flange.
As shown in Figure 14 and Figure 15, partition 34 is formed between pilot hole 311 two neighboring in piston bush 33, on partition 34
Offer the oil-through hole 35 for being connected to two neighboring pilot hole 311.The oil-through hole 35 is used to guarantee that the son of 34 two sides of partition to turn
Axis 10 can smoothly obtain the lubrication of lubricating oil.
Preferably, the axis of oil-through hole 35 is parallel with the axis of sub- shaft 10.
Preferably, the axis of each pilot hole 311 at least two pilot holes 311 is parallel.
As shown in Figure 7 to 10, sub- shaft 10 has the sliding section 11 being slidably matched with piston component, and sliding section 11 is located at
One end of the close cylinder of sub- shaft 10, and section 11 is slid with sliding mating surface 111.Since sub- shaft 10 passes through sliding cooperation
Face 111 and the slip hole 321 of piston 32 be slidably matched, hereby it is ensured that the motion credibility of the two, both effectively avoids stuck.
Especially proximate to the sub- shaft 10 of 60 side of lower flange setting, sliding mating surface 111 in the sub- shaft 10 with it is right
The wall surface of the hole of the slip hole 321 for the piston 32 answered cooperates, so that piston 32 drives the sub- shaft 10 to rotate.
Preferably, there are two symmetrically arranged sliding mating surfaces 111 for sliding section 11 tool.Since sliding mating surface 111 is symmetrical
Setting ensure that sub- shaft 10 and the movement of piston 32 are reliable so that two slide being more uniformly stressed for mating surface 111
Property.
As shown in Figure 7 to 10, sub- shaft 10 has the sliding section 11 being slidably matched with piston component, and sliding section 11 is located at
One end of the close cylinder of sub- shaft 10, and slide symmetrically arranged sliding mating surface 111 there are two the tools of section 11.
Preferably, sliding mating surface 111 is parallel with the axial plane of sub- shaft 10, sliding mating surface 111 and piston 32
The inner wall of slip hole 321 be slidably matched in the axis direction perpendicular to sub- shaft 10.
Sub- shaft 10 in the present invention has oil leab 13, and at least part of oil leab 13 is the interior of sub- shaft 10
Portion's oil duct.Due at least part internal galleries of oil leab 13, thus lubricating oil a lot of leakage effectively is avoided, improves profit
The flowing reliability of lubricating oil.
As shown in Figure 7 to 10, the oil leab 13 at sliding mating surface 111 is external oil duct.Since sliding cooperates
Oil leab 13 at face 111 is external oil duct, so that lubricating oil can be directly fed to sliding mating surface 111 and piston
32, it effectively avoids the two frictional force excessive and wears, to improve the motion smoothing of the two.
Sub- shaft 10 in the present invention has oil-through-hole 14, and internal galleries are connected to by oil-through-hole 14 with external oil duct.By
In being provided with oil-through-hole 14, so that inside and outside oil duct can be smoothly connected to, and passing through can also be to lubricating oil at oil-through-hole 14
Oiling at road 13, to ensure that the oiling convenience of oil leab 13.
As described in Figure 2, the compressor in the present invention further includes support plate 61, and the separate of lower flange 60 is arranged in support plate 61
On the end face of cylinder side, and support plate 61 and the concentric setting of lower flange 60, to support rotating assembly, sub- shaft 10 passes through down
Through-hole on flange 60 is supported in support plate 61, and support plate 61 has the second thrust surface 611 for being used to support sub- shaft 10.By
It is used to support sub- shaft 10 in being provided with support plate 61, thus improves the connection reliability between each component.
Since the setting of support plate 61 is in 60 side of lower flange, thus support plate 61 is mainly used for supporting close to lower flange 60 1
The sub- shaft 10 of side setting, to guarantee its installation reliability.
As shown in Figure 2 and Figure 4, support plate 61 is connect by the 5th fastener 82 with lower flange 60.
Preferably, the 5th fastener 82 is bolt or screw.
Preferably, the support plate screw hole worn there are three being arranged on lower flange 60 for the 5th fastener 82.Lower flange 60
On the circle that is constituted of center of four pump housing screw holes and the mass center of lower flange 60 exist eccentric, eccentricity size is e, this
Amount determines the eccentricity of the assembly of the cylinder close to 60 side of lower flange, rotates a circle in piston bush 33, gas displacement V=2*
2e*S, wherein S is piston main body feature cross-section product；The center of support plate screw hole is overlapped with the axle center of lower flange 60, with
Five fasteners 82 cooperate fixed support plate 61.
As shown in Fig. 2 and Figure 13, support plate 61 is cylindrical structure, is uniformly distributed three screw holes.The end of support plate 61
Face has certain roughness requirements, the bottom surface with the sub- shaft 10 close to 60 side of lower flange.
As shown in Figure 1, the compressor include dispenser component 90, housing unit 91, electric machine assembly 92, pump assembly 93,
Cover assembly 94 and lower cover and mounting plate 95, wherein the outside of housing unit 91, cover assembly 94 is arranged in dispenser component 90
It is assemblied in the upper end of housing unit 91, lower cover and mounting plate 95 are assemblied in the lower end of housing unit 91, electric machine assembly 92 and the pump housing
Component 93 is respectively positioned on the inside of housing unit 91, and the top of pump assembly 93 is arranged in electric machine assembly 92.The pump housing of compressor
Component 93 includes above-mentioned upper flange 50, lower flange 60, cylinder, rotating assembly and piston component.
Preferably, above-mentioned each component is connected by way of welding, hot jacket or cold pressing.
The assembling process of entire pump assembly 93 is as follows: piston 32 is mounted in pilot hole 311, while cylinder and piston set
33 are co-axially mounted, and lower flange 60 is fixed on cylinder, the slip hole 321 of the sliding mating surface 111 and piston 32 of sub- shaft 10
A pair of parallel surface engagement installation, 50 rigid drive shaft of upper flange, while upper flange 50 is fixed on cylinder by screw.
To complete the assembly of pump assembly 93, as shown in Figure 4.
Preferably, the compressor in the present invention is not provided with suction valve chip, so as to effectively reduce inspiratory resistance, improves pressure
The compression efficiency of contracting machine.
It should be noted that in this specific embodiment, when a piston 32 completes movement in one week, meeting air-breathing,
It is vented twice, so that compressor be made to have the characteristics that compression efficiency is high.Compared with the single cylinder roller compressor with discharge capacity, due to inciting somebody to action
First compression originally is divided into two second compressions, thus the torque fluctuations of the compressor in the present invention are relatively small, when operation, has
Exhaust resistance is small, effectively eliminates exhaust noise.
As shown in Figure 19 to Figure 33, the compressor in the present invention further includes the intermediate flow channel 26 being arranged on cylinder, adjacent
Two cylinders are connected to by intermediate flow channel 26.Since two neighboring cylinder can be connected to by intermediate flow channel 26, hereby it is ensured that
The multi-stage compression reliability of compressor.
As shown in Figure 22 to Figure 25, the cylinder wall of the low-pressure stage cylinder 20 at least two cylinders has air inlet 21 and connects
Port 24, communication port 24 pass through the hiigh pressure stage cylinder 200 in the intermediate flow channel 26 and at least two cylinders on low-pressure stage cylinder 20
Intermediate flow channel 26 be connected to, air inlet 21 connect with the dispenser component 90 of compressor.Low-pressure stage cylinder 20 in the present invention
The inner wall of cylinder wall has low-pressure stage air inlet dashpot 29, and low-pressure stage air inlet dashpot 29 is connected to air inlet 21 (to be please referred to
Figure 22 to Figure 25).Due to being provided with low-pressure stage air inlet dashpot 29, thus a large amount of gas can be stored at this, so as to become
Cavity volume 31 can full air-breathing, to enable the enough air-breathings of compressor, and in poor inspiration, can supply and store in time
Gas is to capacity chamber 31, to guarantee the compression efficiency of compressor.
As shown in Figure 22 to Figure 25, low-pressure stage air inlet dashpot 29 is arc-shaped in the sagittal plane of low-pressure stage cylinder 20
Section, and the both ends of low-pressure stage air inlet dashpot 29 are extended from air inlet 21 to 24 position of communication port, and relative into
Port 21, low-pressure stage air inlet dashpot 29 are being less than phase negative side with the arc length of upward extended segment with the rotation direction of piston bush 33
To extended segment arc length.
In the preferred embodiment shown in Figure 22 to Figure 25, the outside wall surface of the cylinder wall of low-pressure stage cylinder 20 has connection
Slot 28, communication port 24 are connected to connectivity slot 28, and compressor further includes sealing plate 81, sealing plate 81 be arranged at the notch of connectivity slot 28 with
Connectivity slot 28 is closed, the intermediate flow channel 26 of connectivity slot 28 and the formation low-pressure stage cylinder 20 of communication port 24.It will be even by sealing plate 81
Through slot 28 is closed to form intermediate flow channel 26, to ensure that the heat-exchange working medium flowed out through communication port 24 can pass through intermediate flow channel
At 26 guiding hiigh pressure stage cylinders 200, to ensure that the functional reliability of compressor.
As shown in Fig. 2, compressor further includes multiple 4th fasteners 83, sealing plate 81 is fixed on cylinder by the 4th fastener 83
On.Preferably, the 4th fastener 83 is screw.
As shown in Figure 19 to Figure 21, the inner wall of the cylinder wall of hiigh pressure stage cylinder 200 has hiigh pressure stage air inlet dashpot 23
With exhaust outlet 22, hiigh pressure stage air inlet dashpot 23 is connected to the intermediate flow channel 26 of hiigh pressure stage cylinder 200, exhaust outlet 22 and compressor
Cavity connection.Due to being provided with hiigh pressure stage air inlet dashpot 23, thus a large amount of gas can be stored at this, so that transfiguration
Product chamber 31 can full air-breathing, to enable the enough air-breathings of compressor, and in poor inspiration, can supply in time and store gas
Body is to capacity chamber 31, to guarantee the compression efficiency of compressor.
Hiigh pressure stage cylinder 200 in the present invention also has gas supplementing opening 27, and gas supplementing opening 27 and hiigh pressure stage air inlet dashpot 23 connect
Logical (please referring to Figure 19 to Figure 21).The gas that the gas and gas supplementing opening 27 being discharged through low-pressure stage cylinder 20 fill into is in hiigh pressure stage air inlet
It is mixed at dashpot 23, to reduce the completion compression in hiigh pressure stage cylinder 200 after suction temperature.
In the preferred embodiment shown in Figure 19 to Figure 21, hiigh pressure stage air inlet dashpot 23 is in hiigh pressure stage cylinder 200
Arc-shaped section in sagittal plane, and the both ends of hiigh pressure stage air inlet dashpot 23 from gas supplementing opening 27 to 22 position of exhaust outlet
Extend, and relative to gas supplementing opening 27, hiigh pressure stage air inlet dashpot 23 with the rotation direction of piston bush 33 with upward extended segment
Arc length be greater than opposite direction extended segment arc length.
Preferably, compressor further includes at least two exhaust valve components 40, is corresponded at communication port 24 and exhaust outlet 22 each
It is provided with an exhaust valve component 40.Since correspondence is each provided with an exhaust valve component at communication port 24 and exhaust outlet 22
40, thus effectively gas in capacity chamber 31 is avoided largely to leak, it ensure that the compression efficiency of capacity chamber 31.
In the preferred embodiment shown in Figure 19, holding tank is offered on the outer wall of the cylinder wall of hiigh pressure stage cylinder 200
25, exhaust outlet 22 penetrates through the slot bottom of holding tank 25, and an exhaust valve component 40 is arranged in holding tank 25.It is used for due to being provided with
The holding tank 25 of exhaust valve component 40 is accommodated, thus reduces the occupied space of exhaust valve component 40, component is set rationally, from
And improve the space utilization rate of cylinder.
Specifically, each exhaust valve component 40 includes exhaust valve plate 41 and valve block baffle 42, exhaust valve plate 41 is blocked
Communication port 24 or exhaust outlet 22, valve block baffle 42 are stacked on exhaust valve plate 41.Due to being provided with valve block baffle 42, thus effectively
It avoids exhaust valve plate 41 from excessively opening, ensure that the exhaust performance of cylinder.
Preferably, exhaust valve plate 41 and valve block baffle 42 are connected by the first fastener 43.Further, the first fastener
43 be screw.
It should be noted that the exhaust valve component 40 in the present invention can be by the outside of capacity chamber 31 and pump assembly 93
Space separates, for back pressure be vented: i.e. when capacity chamber 31 is connected to communication port 24 or exhaust outlet 22 after, the pressure of capacity chamber 31
When power is greater than exterior space pressure (pressure at expulsion), exhaust valve plate 41 is opened, and starts to be vented；If the pressure of capacity chamber 31 after connection
Power is still below pressure at expulsion, then exhaust valve plate 41 does not work at this time.At this point, compressor is remained in operation, is compressed, until capacity chamber
31 are connected to exhaust outlet 22, and the gas in capacity chamber 31 is pressed into exterior space, completes exhaust process.The exhaust of exhaust outlet 22
Mode is forced exhaust mode.
The operation of compressor is specifically introduced below, for rotating clockwise:
As shown in figure 36, the compressor in the present invention is arranged using cross slides principle.Wherein, the axis of sub- shaft 10
Heart O1With the axle center O of cylinder2Eccentric setting, and the eccentricity of the two is fixed as e, and the two is rotated rotating around respective axle center.It is living
Plug 32 is equivalent to sliding blocks in cross slides, the distance and sub- shaft 10 in the axle center of piston bush 33 to the axle center of piston 32
The distance in axle center to the axle center of piston 32 be respectively equivalent to two connecting rod l1、l2, thus constitute the main body of crosshead shoe principle
Structure.
As shown in figure 36, when the operation of the compressor of above structure, axle center O of the sub- shaft 10 around sub- shaft 101Rotation；It is living
Axle center O of the plug sleeve 33 around cylinder 202Rotation, and the axle center of sub- shaft 10 and the axle center eccentric setting and eccentric distance of cylinder 20 are solid
It is fixed；The piston 32 of piston component is under the driving of sub- shaft 10 with the rotation of sub- shaft 10 and simultaneously along the axis perpendicular to sub- shaft 10
Line direction reciprocatingly slides in the piston bush 33 of piston component.
Such as the compressor that the above method is run, cross slides are constituted, which uses cross slides
Principle, wherein piston 32 is used as sliding block, and the sliding mating surface 111 of sub- shaft 10 is used as first connecting rod l1, piston bush 33 guiding
Hole 311 is used as second connecting rod l2(please referring to Figure 36).
Specifically, the axle center O of sub- shaft 101It is equivalent to first connecting rod l1Rotation center, the axle center O of cylinder 202Quite
In second connecting rod l2Rotation center；The sliding mating surface 111 of sub- shaft 10 is equivalent to first connecting rod l1, the guiding of piston bush 33
Hole 311 is equivalent to second connecting rod l2；Piston 32 is equivalent to sliding block.Pilot hole 311 is mutually perpendicular to sliding mating surface 111；Piston
32 can only move back and forth with pilot hole 311 relatively, and piston 32 can only be moved back and forth relative to sliding mating surface 111.32 letter of piston
It turns to after mass center it can be found that its running track is circular motion, which is the axle center O with cylinder 202With the axis of sub- shaft 10
Heart O1Line be diameter circle.
As second connecting rod l2When circling, sliding block can be along second connecting rod l2It moves back and forth；Meanwhile sliding block can edge
First connecting rod l1It moves back and forth.First connecting rod l1With second connecting rod l2Remain vertical, so that sliding block is along first connecting rod l1Back and forth
The direction of motion and sliding block are along second connecting rod l2Vibration-direction is mutually perpendicular to.First connecting rod l1With second connecting rod l2And piston 32
Relative motion relation, formed cross slides principle.
Under the movement technique, sliding block is circled, angular speed and first connecting rod l1With second connecting rod l2Rotation speed
It spends equal.Sliding block running track is circle.The circle is with first connecting rod l1Rotation center and second connecting rod l2Rotation center center
Away from for diameter.
In specific embodiment as shown in Figure 3, two cylinders differ 180 degree interlaced arrangement.Two pistons 32 are reciprocal
Four capacity chambers 31 are formed in motion process.And the corresponding two dispenser components 90 of the two cylinders staggeredly arrange by 180 degree.
It is of course also possible to consider for two dispenser components 90 to be arranged in the same side, in this way, two cylinders also answer dislocation-free to be arranged, it is complete
Full weight is closed stacked.
As shown in Figure 18 and Figure 35, Figure 36, wherein close to the axle center 15 and piston bush axle center of the sub- shaft of lower flange side
Eccentric distance e is differed between 333, piston centroid trajectory line 322 is rounded.
Specifically, electric machine assembly 92 drives the sub- shaft 10 close to 50 side of upper flange to rotate, the sliding of sub- shaft 10
Mating surface 111 drives the piston 32 close to 50 side of upper flange to move, and piston 32 drives piston bush 33 to rotate, and then drives close
The piston 32 of 60 side of lower flange rotates, and the sub- shaft 10 close to 60 side of lower flange is promoted to rotate.In entire moving component
In, piston bush 33 only circles, and 32 one side of piston is moved back and forth relative to sub- shaft 10, while again relative to piston
The pilot hole 311 of set 33 moves back and forth, and two reciprocating motions are mutually perpendicular to and carry out simultaneously, to make the reciprocal of both direction
Movement constitutes cross slides motion mode.The compound motion of this type cross slides makes piston 32 relative to piston bush
33 is reciprocating, and the cavity which form piston bush 33, cylinder and piston 32 periodically becomes larger, reduces.And
Piston 32 is circled relative to cylinder, the capacity chamber 31 which form piston bush 33, cylinder and piston 32
Periodically it is connected to air inlet 21, exhaust outlet 22.Under the collective effect of two above relative motion, keep compressor complete
At air-breathing, the process of compression, exhaust.In the process of reciprocating, the centroid trajectory line of piston 32 is circle, and circular diameter is equal to
Eccentric amount e, the center of circle is on the center of sub- shaft 10 and the midpoint of the line of centres of piston bush 33.
As shown in Figure 29 to Figure 33, Figure 36, by taking a capacity chamber 31 as an example, when capacity chamber 31 is connected to gas supplementing opening 27
When, start air-breathing (please referring to Figure 29 and Figure 30)；Piston bush 33 continues band piston 32, sub- shaft 10 rotates clockwise, and works as change
After cavity volume 31 is detached from gas supplementing opening 27, entire air-breathing terminates, and capacity chamber 31 is fully sealed at this time, starts compression and (please refers to figure
31)；Continue to rotate, gas constantly compresses, and when capacity chamber 31 is connected to exhaust outlet 22, starts to be vented (please referring to Figure 32)；
Continue to rotate, constantly compression while be constantly vented, until capacity chamber 31 completely disengages exhaust outlet 22, complete entire air-breathing,
Compression, exhaust process (please referring to Figure 32 to Figure 33)；Subsequent capacity chamber 31 is again coupled to gas supplementing opening 27 after rotating by a certain angle.
The total displacement of compressor is V=2*2* (2e*S).
In addition, the compressor in the present invention also has the advantages of Zero clearance volume, high volumetric efficiency.
Heat exchange equipment in the present invention further includes First Heat Exchanger 96, the second heat exchanger 97 and four-way valve 98, compressor,
By the formation circulating heat exchanging pipe of four-way valve 98, heat exchange equipment further includes 99 He of flash vessel for one heat exchanger 96 and the second heat exchanger 97
Gas tonifying branch, flash vessel 99 are arranged on circulating heat exchanging pipe and between First Heat Exchanger 96 and the second heat exchanger 97, mend
The first end of gas branch is connected to flash vessel 99, the gas supplementing opening of the hiigh pressure stage cylinder 200 of the second end and compressor of gas tonifying branch
27 connections.
As shown in Fig. 1 and Figure 34, heat exchange equipment further includes increasing enthalpy component 87, gas tonifying branch by increasing enthalpy component 87 and high pressure
The gas supplementing opening 27 of grade cylinder is connected to.
As shown in figure 34, the heat exchange equipment in the present invention further includes first throttle element 84, the second restricting element 85 and cuts
Only valve 86, first throttle element 84 are arranged on circulating heat exchanging pipe and between First Heat Exchanger 96 and flash vessel 99；The
Two restricting elements 85 are arranged on circulating heat exchanging pipe and between the second heat exchanger 97 and flash vessel 99；Shut-off valve 86 is arranged
In gas tonifying branch, to control the on-off of gas tonifying branch.
There are two types of operating modes, including refrigeration mode and heating mode for heat exchange equipment tool in the present invention, in refrigeration mode
Under, heat-exchange working medium enters First Heat Exchanger 96 (i.e. condenser) under the action of compressor, through four-way valve 98, and through first throttle
Element 84 throttles, which is level-one throttling, and the heat-exchange working medium after level-one throttling enters flash vessel 99 by the first fluid-through port, and
It constantly absorbs heat on the top of the flash distillation chamber of flash vessel 99, shwoot, the gaseous state heat-exchange working medium after shwoot passes through the blow vent stream at top
At the gas supplementing opening 27 for entering the hiigh pressure stage cylinder 200 of compressor, temperature after the heat-exchange working medium heat release of the lower part of the flash distillation chamber of flash vessel 99
Degree reduces, and forms the heat-exchange working medium of supercooled liquid, and the heat-exchange working medium of supercooled liquid enters the second throttling member by the second fluid-through port
In part 85, and enter the second heat exchanger 97 (i.e. evaporator) after the throttling of the second restricting element 85, is flowed finally by four-way valve 98
It is back in compressor；In a heating mode, heat-exchange working medium enters the second heat exchanger 97 through four-way valve 98 under the action of compressor
(i.e. condenser), and throttle through the second restricting element 85, which is that level-one throttles, and the heat-exchange working medium after level-one throttling passes through the
Two fluid-through ports enter flash vessel 99, and the heat-exchange working medium on the top of the flash distillation chamber of flash vessel 99 constantly absorbs heat, shwoot, after shwoot
Gaseous state heat-exchange working medium flowed by the blow vent at the top of flash vessel 99 compressor hiigh pressure stage cylinder 200 gas supplementing opening 27
Place, temperature reduces after the heat-exchange working medium heat release of the lower part of the flash distillation chamber of flash vessel 99, forms the heat-exchange working medium of supercooled liquid, is subcooled
The heat-exchange working medium of liquid enters first throttle element 84 by the first fluid-through port, enters first after the throttling of first throttle element 84
Heat exchanger 96 (i.e. evaporator), flows back into compressor finally by four-way valve 98, and heat exchange equipment is mentioned by two stages of compression increasing enthalpy
The high runnability of heat exchange equipment.
In addition, the compressor in the present invention uses two-stage enthalpy increasing technology, the low temperature system of compressor and heat exchange equipment is improved
Heat, high-temperature refrigeration ability, improve the reliability and Energy Efficiency Ratio of system.
It should be noted that term used herein above is merely to describe specific embodiment, and be not intended to restricted root
According to the illustrative embodiments of the application.As used herein, unless the context clearly indicates otherwise, otherwise singular
Also it is intended to include plural form, additionally, it should be understood that, when in the present specification using term "comprising" and/or " packet
Include " when, indicate existing characteristics, step, work, device, component and/or their combination.
It should be noted that the description and claims of this application and term " first " in above-mentioned attached drawing, "
Two " etc. be to be used to distinguish similar objects, without being used to describe a particular order or precedence order.It should be understood that using in this way
Data be interchangeable under appropriate circumstances, so that presently filed embodiment described herein can be in addition to illustrating herein
Or the sequence other than those of description is implemented.
The foregoing is only a preferred embodiment of the present invention, is not intended to restrict the invention, for the skill of this field
For art personnel, the invention may be variously modified and varied.All within the spirits and principles of the present invention, made any to repair
Change, equivalent replacement, improvement etc., should all be included in the protection scope of the present invention.
Claims (34)
1. a kind of compressor characterized by comprising
Upper flange (50)；
Lower flange (60)；
Two cylinders, described two cylinders are folded between the upper flange (50) and the lower flange (60), two neighboring institute
Cylinder is stated to be interconnected so that compressor forms compound compressor；
Rotating assembly, the rotating assembly sequentially passes through the upper flange (50), the cylinder and the lower flange (60), described
Rotating assembly includes the sub- shaft (10) being arranged in a one-to-one correspondence with each of described two cylinders cylinder, the sub- shaft
(10) the axle center eccentric setting and eccentric distance of axle center cylinder corresponding with sub- shaft (10) described in this are fixed；
Piston component, the piston component have and each one-to-one capacity chamber (31) of cylinder, the piston group
Part is pivotally disposed in the cylinder, and at least one described sub- shaft (10) is drivingly connected with the piston component to change
Become the volume of the capacity chamber (31), the piston component includes:
Piston bush (33), the piston bush (33) are pivotally disposed in the cylinder；
Piston (32), the piston (32) are slidably arranged in the piston bush (33) to form the capacity chamber (31), and
The capacity chamber (31) is located in the glide direction of the piston (32), the cylinder, the sub- shaft (10), the piston
It (32) is respectively two,
One sub- shaft (10) is driving shaft, passes through the upper flange (50) and protrudes into close to the upper flange (50) side
In the cylinder, and moves and connect with the piston (32) in cylinder described in this；
Another described sub- shaft (10) is driven axle, passes through the lower flange (60) and protrudes into close to the lower flange (60) side
The cylinder in, and move and connect with the piston (32) in cylinder described in this, the piston (32) is cylindrical.
2. compressor according to claim 1, which is characterized in that rotation is driven by motor in the driving shaft, described passive
Axis drives rotation by the driving shaft indirectly.
3. compressor according to claim 2, which is characterized in that the piston (32) has along the sub- shaft (10)
Axially through the slip hole (321) of setting, the sub- shaft (10) passes through the slip hole (321),
With the piston (32) of driving shaft cooperation under the driving of the driving shaft with the spindle rotation and simultaneously
It reciprocatingly slides in the piston bush (33) along the axis direction perpendicular to the driving shaft；
With the piston (32) of driven axle cooperation, revolved under the driving of the piston bush (33) with the piston bush (33)
Turn and the driven axle is driven to rotate, while with the piston (32) of driven axle cooperation along perpendicular to the driven axle
Axis direction reciprocatingly slides in the piston bush (33).
4. compressor according to claim 3, which is characterized in that the slip hole (321) is rectangle long hole or kidney slot.
5. compressor according to claim 1, which is characterized in that the piston (32) has along the piston (32)
The inner surface adaptability of symmetrically arranged a pair of of the curved surfaces of vertical plane, the curved surfaces and the cylinder cooperates, and the arc
Two times of the cambered surface radius of curvature on shape surface are equal to the internal diameter of the cylinder.
6. compressor according to claim 1, which is characterized in that have in the piston bush (33) along the piston bush
(33) pilot hole (311) of radial perforation setting, the pilot hole (311) is two, right in each pilot hole (311)
It should be provided with the piston (32), the piston (32) is slidably arranged in the pilot hole (311) and is transported with reciprocating linear
It is dynamic.
7. compressor according to claim 6, which is characterized in that the axis of each pilot hole (311) is parallel.
8. compressor according to claim 6, which is characterized in that the two neighboring guiding in the piston bush (33)
Partition (34) are formed between hole (311), are offered on the partition (34) for being connected to the two neighboring pilot hole (311)
Oil-through hole (35).
9. compressor according to claim 8, which is characterized in that the axis of the oil-through hole (35) and the sub- shaft
(10) axis is parallel.
10. compressor according to claim 6, which is characterized in that the pilot hole (311) is at the lower flange (60)
Orthographic projection there is a pair of parallel straightway, the pair of parallel straightway is a pair of of phase of the piston bush (33)
Parallel inner wall projects to be formed, and the piston (32) has and the pair of parallel inner wall of the pilot hole (311)
Face shape is adapted and slides the outer mold surface of cooperation.
11. compressor according to claim 1, which is characterized in that the piston bush (33) towards the lower flange
(60) the first thrust surface (332) of side is contacted with the surface of the lower flange (60).
12. compressor according to claim 2, which is characterized in that the sub- shaft (10) has and the piston component
The sliding section (11) being slidably matched, sliding section (11) are located at one end close to the cylinder of the sub- shaft (10), and
The sliding section (11) has sliding mating surface (111).
13. compressor according to claim 12, which is characterized in that the sliding mating surface (111) is symmetricly set on institute
State the two sides of sliding section (11).
14. compressor according to claim 13, which is characterized in that the sliding mating surface (111) and the sub- shaft
(10) axial plane is parallel, the inner wall of the slip hole (321) of sliding mating surface (111) and the piston (32)
Face is slidably matched on the axis direction perpendicular to the sub- shaft (10).
15. according to claim 1 to compressor described in any one of 14, which is characterized in that the compressor further includes setting
Intermediate flow channel (26) on the cylinder, the two neighboring cylinder are connected to by the intermediate flow channel (26).
16. compressor according to claim 15, which is characterized in that low-pressure stage cylinder (20) in described two cylinders
Cylinder wall has air inlet (21) and communication port (24), and the communication port (24) passes through the centre on the low-pressure stage cylinder (20)
Runner (26) is connected to the intermediate flow channel (26) of the hiigh pressure stage cylinder (200) in described two cylinders.
17. compressor according to claim 16, which is characterized in that the inner wall of the cylinder wall of the low-pressure stage cylinder (20)
Face has low-pressure stage air inlet dashpot (29), and the low-pressure stage air inlet dashpot (29) is connected to the air inlet (21).
18. compressor according to claim 17, which is characterized in that the low-pressure stage air inlet dashpot (29) is described low
It arbitrarily downgrades in the sagittal plane of cylinder (20) arc-shaped section, and the both ends of the low-pressure stage air inlet dashpot (29) are by the air inlet
Extend at mouth (21) to the communication port (24) position.
19. compressor according to claim 16, which is characterized in that the outer wall of the cylinder wall of the low-pressure stage cylinder (20)
Face has connectivity slot (28), and the communication port (24) is connected to the connectivity slot (28), and the compressor further includes sealing plate (81),
The sealing plate (81) is arranged at the notch of the connectivity slot (28) to close the connectivity slot (28), the connectivity slot (28)
The intermediate flow channel (26) of the low-pressure stage cylinder (20) is formed with the communication port (24).
20. compressor according to claim 16, which is characterized in that the cylinder wall of the hiigh pressure stage cylinder (200) it is interior
Wall surface has hiigh pressure stage air inlet dashpot (23) and exhaust outlet (22), the hiigh pressure stage air inlet dashpot (23) and the hiigh pressure stage
The intermediate flow channel (26) of cylinder (200) is connected to, and the exhaust outlet (22) is connected to the cavity of the compressor.
21. compressor according to claim 20, which is characterized in that the hiigh pressure stage cylinder (200) also has gas supplementing opening
(27), the gas supplementing opening (27) is connected to the hiigh pressure stage air inlet dashpot (23).
22. compressor according to claim 21, which is characterized in that the hiigh pressure stage air inlet dashpot (23) is in the height
It arbitrarily downgrades in the sagittal plane of cylinder (200) arc-shaped section, and the both ends of the hiigh pressure stage air inlet dashpot (23) are by the benefit
Extend at port (27) to the exhaust outlet (22) position.
23. compressor according to claim 12, which is characterized in that the sub- shaft (10) has oil leab (13),
The oil leab (13) includes setting in the internal internal galleries of the sub- shaft (10) and is arranged in the sliding mating surface
(111) oil-through-hole (14) of external oil duct and the connection internal galleries and the external oil duct at.
24. according to claim 1 to compressor described in any one of 14, which is characterized in that the two neighboring cylinder is each other
Concentric setting.
25. compressor according to claim 24, which is characterized in that the axle center of the upper flange (50) and on described
The axle center eccentric setting of the cylinder of flange (50) side setting.
26. compressor according to claim 25, which is characterized in that the axle center of the lower flange (60) and under described
The axle center eccentric setting of the cylinder of flange (60) side setting.
27. according to claim 1 to compressor described in any one of 14, which is characterized in that the compressor further includes support
Plate (61), support plate (61) setting is on the end face far from the cylinder side of the lower flange (60), and the branch
To support the rotating assembly, the support plate (61) has for branch for fagging (61) and the lower flange (60) concentric setting
Support the second thrust surface (611) of the rotating assembly.
28. compressor according to claim 20, which is characterized in that the compressor further includes at least two exhaust valve groups
Correspondence is each provided with the exhaust valve component (40) at part (40), the communication port (24) and the exhaust outlet (22).
29. compressor according to claim 28, which is characterized in that outside the cylinder wall of the hiigh pressure stage cylinder (200)
It is offered on wall holding tank (25), the exhaust outlet (22) penetrates through the slot bottom of the holding tank (25), an exhaust valve group
Part (40) setting is in the holding tank (25).
30. compressor according to claim 28, which is characterized in that each exhaust valve component (40) includes:
Exhaust valve plate (41), the exhaust valve plate (41) block the communication port (24) or the exhaust outlet (22)；
Valve block baffle (42), the valve block baffle (42) are stacked on the exhaust valve plate (41).
31. a kind of heat exchange equipment, including compressor, which is characterized in that the compressor is any one of claims 1 to 30 institute
The compressor stated.
32. heat exchange equipment according to claim 31, which is characterized in that the heat exchange equipment further includes First Heat Exchanger
(96), the second heat exchanger (97) and four-way valve (98), the compressor, the First Heat Exchanger (96) and second heat exchanger
(97) circulating heat exchanging pipe, the heat exchange equipment are formed by the four-way valve (98) further include:
Flash vessel (99), the flash vessel (99) are arranged on the circulating heat exchanging pipe and are located at the First Heat Exchanger (96)
Between second heat exchanger (97)；
Gas tonifying branch, the first end of the gas tonifying branch are connected to the flash vessel (99), the second end of the gas tonifying branch with
The gas supplementing opening (27) of the hiigh pressure stage cylinder (200) of the compressor is connected to.
33. a kind of operation method of compressor, which is characterized in that the compressor is described in any one of claims 1 to 30
Compressor, the operation method includes:
Axle center O of the sub- shaft (10) around the sub- shaft (10)1Rotation；
Axle center O of the piston bush (33) around the cylinder (20)2Rotation, and the axle center of the sub- shaft (10) and the cylinder (20)
Axle center eccentric setting and eccentric distance fix；
The piston (32) of piston component is under the driving of the sub- shaft (10) with sub- shaft (10) rotation and simultaneously along vertical
Directly reciprocatingly slide in the piston bush (33) of the piston component in the axis direction of the sub- shaft (10).
34. operation method according to claim 33, which is characterized in that the operation method is former using cross slides
Reason, wherein the piston (32) is used as sliding block, and the sliding mating surface (111) of the sub- shaft (10) is used as first connecting rod l1, institute
The pilot hole (311) of piston bush (33) is stated as second connecting rod l2。
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| CN201510482483.8A CN106438359B (en) | 2015-08-07 | 2015-08-07 | The operation method of compressor, heat exchange equipment and compressor |
| PCT/CN2016/084329 WO2017024866A1 (en) | 2015-08-07 | 2016-06-01 | Compressor, heat exchanging apparatus, and operating method for compressor |
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| CN201510482483.8A CN106438359B (en) | 2015-08-07 | 2015-08-07 | The operation method of compressor, heat exchange equipment and compressor |
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| CN106438356B (en) * | 2015-08-07 | 2019-01-08 | 珠海格力电器股份有限公司 | The operation method of compressor, heat exchange equipment and compressor |
| CN107327997B (en) * | 2017-08-01 | 2023-09-08 | 广东美的制冷设备有限公司 | Air conditioning system |
| CN107559176B (en) * | 2017-08-22 | 2024-02-27 | 珠海格力电器股份有限公司 | Pump body assembly and compressor with same |
| CN108061039A (en) * | 2017-10-23 | 2018-05-22 | 武汉凌达压缩机有限公司 | The gas supplementary structure and compressor of compressor |
| CN116241471A (en) * | 2021-12-07 | 2023-06-09 | 珠海格力电器股份有限公司 | Fluid machine and heat exchange device |
| CN117145768A (en) * | 2022-05-23 | 2023-12-01 | 珠海格力电器股份有限公司 | Fluid machine and heat exchange device |
| CN117145766A (en) * | 2022-05-23 | 2023-12-01 | 珠海格力电器股份有限公司 | Fluid machine and heat exchange device |
| CN115711213A (en) * | 2022-12-06 | 2023-02-24 | 郑州轻工业大学 | Rotary piston type air supply compressor with adjustable inner volume ratio and air conditioning system |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1239757A (en) * | 1998-06-22 | 1999-12-29 | 三星电子株式会社 | Rotary compressor having plurality of compression chambers for multistage compression |
| WO2002012723A1 (en) * | 2000-08-03 | 2002-02-14 | Alan Paul Troup | Multi-stage dry vacuum pump |
| CN2688922Y (en) * | 2004-02-24 | 2005-03-30 | 刘军科 | Air compressor with double rotary cylinders |
| CN103574852A (en) * | 2012-08-02 | 2014-02-12 | 珠海格力电器股份有限公司 | Air conditioner circulating system and method for controlling air supply amount of dual-stage compressor |
| CN104454021A (en) * | 2014-11-15 | 2015-03-25 | 周觉明 | Hydrodynamic machine with rotating wheel and piston synchronized rotary mechanism |
| CN204371674U (en) * | 2014-12-24 | 2015-06-03 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor |
| CN204877941U (en) * | 2015-08-07 | 2015-12-16 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and indirect heating equipment |
| CN106438356A (en) * | 2015-08-07 | 2017-02-22 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor, heat exchange equipment and running method of compressor |
Family Cites Families (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS57158385U (en) * | 1981-03-31 | 1982-10-05 | ||
| JPS59155580A (en) * | 1983-02-25 | 1984-09-04 | Hitachi Ltd | Capacity control type compressor |
| JPS59145379A (en) * | 1983-02-04 | 1984-08-20 | Hitachi Ltd | Fluid machine |
| JPS6062601A (en) * | 1983-09-17 | 1985-04-10 | Masahiro Funaya | Roatry mechanism making relative reciprocating motion |
| JPH06272671A (en) * | 1993-03-16 | 1994-09-27 | Nippon Haazen Kk | Rotary piston machine |
| JP2001065472A (en) * | 1999-08-26 | 2001-03-16 | Isao Suzuki | Pump structure |
| US20080019849A1 (en) * | 2006-07-19 | 2008-01-24 | Chien-Ming Huang | Pumping device |
| JP2011085128A (en) * | 2009-10-16 | 2011-04-28 | Naoya Togashi | Rotary pump |
| JP2012087772A (en) * | 2010-10-15 | 2012-05-10 | Naoya Togashi | Rotary pump |
| CN205064265U (en) * | 2015-08-07 | 2016-03-02 | 珠海格力节能环保制冷技术研究中心有限公司 | Fluid machinery and indirect heating equipment |
-
2015
- 2015-08-07 CN CN201510482483.8A patent/CN106438359B/en active Active
-
2016
- 2016-06-01 WO PCT/CN2016/084329 patent/WO2017024866A1/en active Application Filing
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1239757A (en) * | 1998-06-22 | 1999-12-29 | 三星电子株式会社 | Rotary compressor having plurality of compression chambers for multistage compression |
| WO2002012723A1 (en) * | 2000-08-03 | 2002-02-14 | Alan Paul Troup | Multi-stage dry vacuum pump |
| CN2688922Y (en) * | 2004-02-24 | 2005-03-30 | 刘军科 | Air compressor with double rotary cylinders |
| CN103574852A (en) * | 2012-08-02 | 2014-02-12 | 珠海格力电器股份有限公司 | Air conditioner circulating system and method for controlling air supply amount of dual-stage compressor |
| CN104454021A (en) * | 2014-11-15 | 2015-03-25 | 周觉明 | Hydrodynamic machine with rotating wheel and piston synchronized rotary mechanism |
| CN204371674U (en) * | 2014-12-24 | 2015-06-03 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor |
| CN204877941U (en) * | 2015-08-07 | 2015-12-16 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and indirect heating equipment |
| CN106438356A (en) * | 2015-08-07 | 2017-02-22 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor, heat exchange equipment and running method of compressor |
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|---|---|
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| CN106438359A (en) | 2017-02-22 |
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