CN204877942U - Compressor and indirect heating equipment - Google Patents
Compressor and indirect heating equipment Download PDFInfo
- Publication number
- CN204877942U CN204877942U CN201520594254.0U CN201520594254U CN204877942U CN 204877942 U CN204877942 U CN 204877942U CN 201520594254 U CN201520594254 U CN 201520594254U CN 204877942 U CN204877942 U CN 204877942U
- Authority
- CN
- China
- Prior art keywords
- piston
- cylinder
- sub
- rotating shaft
- compressor
- 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.)
- Active
Links
Landscapes
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
The utility model provides a compressor and indirect heating equipment. The compressor includes: go up the flange, the lower flange, two at least cylinders, two at least cylinder clamps are established between last flange and lower flange, and arbitrary two adjacent cylinders are autonomous working each other all, pivot subassembly, pivot subassembly pass flange, cylinder and lower flange in proper order, the pivot subassembly include with at least two cylinders in the sub - pivot that sets up of every cylinder one -to -one, the axle center eccentric settings and the eccentric distance of the cylinder that axle center and this sub - pivot of sub - pivot correspond fix, piston assembly, piston assembly have with the long -pending chamber of the varactor of every cylinder one -to -one, but piston assembly pivot ground set up in the cylinder, and at least one sub - pivot drives the volume of being connected with change volume chamber with piston assembly. The utility model provides a compressor vibration is little to the volume change of guaranteeing the long -pending chamber of varactor has the law, reduces clearance volume, thereby has improved the operating stability and the operational reliability of compressor.
Description
Technical field
The utility model relates to heat-exchange system technical field, in particular to a kind of compressor and heat transmission equipment.
Background technique
Compressor of the prior art comprises compressor and decompressor etc.For compressor.
The sub-rotating shaft of piston compressor of the prior art and cylinder are in movement process, and the position of the barycenter of the two is change.Motor driven crankshafts outputting power, carrys out pressurized gas by crankshaft driving piston to-and-fro motion in cylinder or liquid does work, to reach the object of pressurized gas or liquid.
There is many defects in traditional piston compressor: due to the existence of suction valve chip and exhaust valve plate, causes inhaling, exhaust resistance strengthens, add suction and discharge noise simultaneously; Lateral force suffered by the cylinder of compressor is comparatively large, and lateral force flogs a dead horse, and reduces compressor efficiency; Bent axle drives reciprocating motion of the pistons, and eccentric mass is comparatively large, causes vibration of compressor large; Compressor drives one or more pistons work by connecting rod, complex structure; The lateral force that bent axle and piston are subject to is comparatively large, and piston easily weares and teares, and causes piston seal performance to reduce.And existing compressor is owing to existing clearance volume, leaks the reasons such as large, volumetric efficiency is low, and has been difficult to further raising.
Moreover, the barycenter of the eccentric part in piston compressor moves in a circle the centrifugal force that generation size is constant, direction changes, and this centrifugal force causes vibration of compressor to aggravate.
Model utility content
Main purpose of the present utility model is to provide a kind of compressor and heat transmission equipment, there is to solve compressor of the prior art the problem that motion is unstable, vibration is large, there is clearance volume.
To achieve these goals, according to an aspect of the present utility model, provide a kind of compressor, comprising: upper flange; Lower flange; At least two cylinders, at least two cylinders are folded between upper flange and lower flange, and arbitrary neighborhood two cylinders work all independently of one another; Rotating assembly, rotating assembly is successively through upper flange, cylinder and lower flange, rotating assembly comprises the sub-rotating shaft arranged with each cylinder one_to_one corresponding at least two cylinders, and the axle center eccentric setting of the cylinder that the axle center of sub-rotating shaft is corresponding with this sub-rotating shaft and eccentric distance are fixed; Piston assembly, piston assembly has and each cylinder capacity chamber one to one, and piston assembly is arranged in cylinder pivotly, and at least one sub-rotating shaft drives with piston assembly the volume be connected to change capacity chamber.
Further, piston assembly comprises: piston sleeve, and piston sleeve is arranged in cylinder pivotly; At least two pistons, piston is slidably arranged in form capacity chamber in piston sleeve, and capacity chamber is positioned in the glide direction of piston.
Further, cylinder, sub-rotating shaft, piston are respectively two, and a sub-rotating shaft is driving shaft, stretch in the cylinder of upper flange side, and be connected with the piston movement in this cylinder through upper flange; Another sub-rotating shaft is driven axle, stretches in the cylinder of lower flange side, and be connected with the piston movement in this cylinder through lower flange.
Further, driving shaft is driven by motor and rotates, and driven axle drives rotation indirectly by driving shaft.
Further, piston has the slip hole of the through setting of axis along sub-rotating shaft, sub-rotating shaft is through slip hole, and the piston coordinated with driving shaft rotates with driving shaft and reciprocatingly slides in piston sleeve along the axial direction perpendicular to driving shaft simultaneously under the driving of driving shaft; The piston coordinated with driven axle, rotates with piston sleeve and drives driven axle to rotate under the driving of piston sleeve, and the piston simultaneously coordinated with driven axle reciprocatingly slides in piston sleeve along the axial direction perpendicular to driven axle.
Further, slip hole is elongated hole or waist shaped hole.
Further, piston has symmetrically arranged a pair arcuate surface of middle vertical plane along piston, and arcuate surface coordinates with the internal surface adaptability of cylinder, and two times of the cambered surface radius of curvature of the arcuate surface internal diameters equaling cylinder.
Further, piston is cylindricality.
Further, have the pilot hole of the through setting of radial direction along piston sleeve in piston sleeve, pilot hole is at least two, and in each pilot hole, correspondence is provided with a piston, and piston is slidably arranged in pilot hole with linear reciprocating motion.
Further, the axis of each pilot hole is all parallel.
Further, in piston sleeve, forming dividing plate between adjacent two pilot holes, dividing plate offering the oil-through hole for being communicated with adjacent two pilot holes.
Further, the axis of oil-through hole parallels with the axis of sub-rotating shaft.
Further, pilot hole has the straightway paralleled for a pair in the orthographic projection at lower flange place, the straightway paralleled for a pair is that the internal face projection that a pair of piston sleeve parallels is formed, and piston has the outer mold surface that the suitable and slippage of the internal face shape paralleled with a pair of pilot hole coordinates.
Further, piston sleeve towards the first thrust surface of lower flange side and the surface contact of lower flange.
Further, sub-rotating shaft has the slippage section be slidably matched with piston assembly, and slippage section is positioned at one end of the close cylinder of sub-rotating shaft, and slippage section has slippage fitting surface.
Further, slippage fitting surface is symmetricly set on the both sides of slippage section.
Further, slippage fitting surface parallels with the axial plane of sub-rotating shaft, and the internal face of the slip hole of slippage fitting surface and piston is slidably matched on the axial direction perpendicular to sub-rotating shaft.
Further, sub-rotating shaft has oil leab, and oil leab comprises the internal galleries that is arranged on sub-rotating shaft inside and is arranged on the outside oil duct at slippage fitting surface place and is communicated with the oil through of internal galleries and outside oil duct.
Further, adjacent two cylinders heart setting coaxially to each other.
Further, the axle center of upper flange and the axle center eccentric setting of the cylinder arranged near upper flange side.
Further, the axle center of lower flange and the axle center eccentric setting of the cylinder arranged near lower flange side.
Further, compressor also comprises dunnage, and dunnage is arranged on the end face away from cylinder side of lower flange, and dunnage and lower flange concentric arrange with supporting revolving shaft assembly, and dunnage has the second thrust surface for supporting revolving shaft assembly.
Further, the cylinder wall of each cylinder has compressed air inlet and the first compression exhaust mouth, when piston assembly is in Inlet Position, and compressed air inlet and the conducting of capacity chamber; When piston assembly is in exhaust position, capacity chamber and the first compression exhaust mouth conducting.
Further, the internal face of cylinder wall has compress inlet air dashpot, and compress inlet air dashpot is communicated with compressed air inlet.
Further, compress inlet air dashpot in the radial plane of cylinder curved section, and compress inlet air dashpot is extended to the first compression exhaust mouth side by compressed air inlet.
Further, the cylinder wall of each cylinder has the second compression exhaust mouth, second compression exhaust mouth is between compressed air inlet and the first compression exhaust mouth, and in the process of piston assembly rotation, first all discharged by the first compression exhaust mouth again after the pressure release of the second compression exhaust mouth at the portion gas in piston assembly.
Further, compressor also comprises exhaust valve component, and exhaust valve component is arranged on the second compression exhaust mouth place.
Further, the outer wall of cylinder wall offers receiving groove, the bottom land of the through receiving groove of the second compression exhaust mouth, exhaust valve component is arranged in receiving groove.
Further, exhaust valve component comprises: exhaust valve plate, and exhaust valve plate to be arranged in receiving groove and to block the second compression exhaust mouth; Valve block baffle plate, valve block baffle plate is stacked on exhaust valve plate.
According to another aspect of the present utility model, provide a kind of heat transmission equipment, comprise compressor, compressor is above-mentioned compressor.
Application the technical solution of the utility model, work all independently of one another between arbitrary neighborhood two cylinders, by eccentric distance is fixed by the axle center eccentric setting of cylinder corresponding with this sub-rotating shaft for the axle center of the sub-rotating shaft in rotating assembly, thus sub-rotating shaft and cylinder are rotated around respective axle center in movement process, and centroid position is constant, when thus making piston assembly move in cylinder, can stablize and rotate continuously, effectively alleviate the vibration of compressor, and ensure that the volume-variation in capacity chamber has rule, reduce clearance volume, thus improve the operation stability of compressor, and then improve the functional reliability of heat transmission equipment.
Accompanying drawing explanation
The Figure of description forming a application's part is used to provide further understanding of the present utility model, and schematic description and description of the present utility model, for explaining the utility model, is not formed improper restriction of the present utility model.In the accompanying drawings:
Fig. 1 shows the structural representation of the compressor in the utility model;
Fig. 2 shows the explosive view of the pump assembly in the utility model;
Fig. 3 shows the installation relation schematic diagram of sub-rotating shaft in the utility model, upper flange, cylinder and lower flange;
Fig. 4 a shows the internal structure schematic diagram of Fig. 3;
Fig. 4 b shows the structural representation of another angle of Fig. 4 a;
Fig. 5 shows the installation relation schematic diagram of exhaust valve component in the utility model and cylinder;
Fig. 6 shows the structural representation of the sub-rotating shaft of the close upper flange side in the utility model;
Fig. 7 shows the internal structure schematic diagram of the sub-rotating shaft in Fig. 6;
Fig. 8 shows the structural representation of the sub-rotating shaft of the close lower flange side in the utility model;
Fig. 9 shows the internal structure schematic diagram of the sub-rotating shaft in Fig. 8;
Figure 10 shows the structural representation of the piston in the utility model;
Figure 11 shows the structural representation of another angle of the piston in Figure 10;
Figure 12 shows the structural representation of the piston sleeve in the utility model;
Figure 13 shows the sectional view of the piston sleeve in the utility model;
Figure 14 shows the structural representation of the upper flange in the utility model;
Figure 15 shows the structural representation of the lower flange in the utility model;
Figure 16 shows the axle center of the sub-rotating shaft of the close lower flange side at the lower flange place of Figure 15 and the eccentric relation schematic diagram in piston sleeve axle center;
Figure 17 piston shown in the utility model is in the working state schematic representation prepared when starting air-breathing;
Figure 18 piston shown in the utility model is in the working state schematic representation in breathing process;
Figure 19 piston shown in the utility model is in working state schematic representation when air-breathing completes;
Working state schematic representation when Figure 20 piston shown in the utility model is in gas compression and is vented from the second compression exhaust mouth;
Figure 21 piston shown in the utility model is in the working state schematic representation in exhaust process;
Figure 22 piston shown in the utility model is in working state schematic representation when will be vented;
Figure 23 piston shown in the utility model is in working state schematic representation when being vented;
Figure 24 shows the fundamental diagram of the compressor in the utility model.
Wherein, above-mentioned accompanying drawing comprises the following drawings mark:
10, sub-rotating shaft; 11, slippage section; 111, slippage fitting surface; 13, oil leab; 14, oil through; The axle center of the sub-rotating shaft 15, near lower flange side; 20, cylinder; 21, compressed air inlet; 22, the first compression exhaust mouth; 23, compress inlet air dashpot; 24, the second compression exhaust mouth; 25, receiving groove; 30, piston assembly; 31, capacity chamber; 311, pilot hole; 32, piston; 321, slip hole; 33, piston sleeve; 332, the first thrust surface; 333, piston sleeve axle center; 34, dividing plate; 35, oil-through hole; 40, exhaust valve component; 41, exhaust valve plate; 42, valve block baffle plate; 43, the first fastening piece; 50, upper flange; 60, lower flange; 61, dunnage; 611, the second thrust surface; 70, the second fastening piece; 80, the 3rd fastening piece; 82, the 4th fastening piece; 90, liquor separator parts; 91, frame set; 92, electric machine assembly; 93, pump assembly; 94, cover assembly; 95, lower cover and mounting plate.
Embodiment
It should be noted that, when not conflicting, the embodiment in the application and the feature in embodiment can combine mutually.Below with reference to the accompanying drawings and describe the utility model in detail in conjunction with the embodiments.
It is noted that following detailed description is all exemplary, be intended to provide further instruction to the application.Unless otherwise, all technology used herein and scientific terminology have the identical meanings usually understood with the application person of an ordinary skill in the technical field.
In the utility model, when not doing contrary explanation, the noun of locality of use is if " left and right " is normally for shown in the drawings left and right; " inside and outside " refers to profile inside and outside relative to each parts itself, but the above-mentioned noun of locality is not limited to the utility model.
There is to solve compressor of the prior art the problem that motion is unstable, vibration is large, there is clearance volume, the utility model provides a kind of compressor and heat transmission equipment, and wherein, heat transmission equipment comprises following compressor.In addition, a kind of operation method of compressor is additionally provided.
As shown in Fig. 2 to Figure 23, compressor comprises upper flange 50, lower flange 60, at least two cylinders 20, rotating assembly and piston assembly 30, at least two cylinders 20 are folded between upper flange 50 and lower flange 60, arbitrary neighborhood two cylinders 20 work all independently of one another, rotating assembly is successively through upper flange 50, cylinder 20 and lower flange 60, rotating assembly comprises the sub-rotating shaft 10 arranged with each cylinder 20 one_to_one corresponding at least two cylinders 20, the axle center eccentric setting of the cylinder 20 that the axle center of sub-rotating shaft 10 is corresponding with this sub-rotating shaft 10 and eccentric distance are fixed, piston assembly 30 has and each cylinder 20 capacity chamber 31 one to one, piston assembly 30 is arranged in cylinder 20 pivotly, and at least one sub-rotating shaft 10 drives with piston assembly 30 volume be connected to change capacity chamber 31.Wherein, upper flange 50 is fixed by the second fastening piece 70 and the cylinder 20 near upper flange 50 side, and lower flange 60 is fixed by the 3rd fastening piece 80 and the cylinder 20 near lower flange 60 side.
Preferably, the second fastening piece 70 and/or the 3rd fastening piece 80 are screw or bolt.
Preferably, upper flange 50 is provided with the first pump housing screw hole worn for the second fastening piece 70.Lower flange 60 is provided with the second pump housing screw hole that four confessions the 3rd fastening piece 80 wears.
It should be noted that, there is certain eccentric distance e in the center of the first pump housing screw hole on upper flange 50 and the barycenter of upper flange 50.This throw of eccentric determines the discharge capacity of the cylinder 20 near upper flange 50 side, and when cylinder 20 rotates a circle, gas displacement is V=2*2e*S, and wherein S is that piston main body feature cross-section amasss.
Work all independently of one another between arbitrary neighborhood two cylinders 20, by eccentric distance is fixed by the axle center eccentric setting of cylinder 20 corresponding for sub-to the axle center of the sub-rotating shaft 10 in rotating assembly and this rotating shaft 10, thus sub-rotating shaft 10 and cylinder 20 are rotated around respective axle center in movement process, and centroid position is constant, when thus making piston assembly 30 move in cylinder, can stablize and rotate continuously, effectively alleviate the vibration of compressor, and ensure that the volume-variation in capacity chamber 31 has rule, reduce clearance volume, thus improve the operation stability of compressor, and then improve the functional reliability of heat transmission equipment.
It should be noted that, adjacent two cylinders 20 coaxially to each other heart are arranged.Preferably, the axle center of upper flange 50 and the axle center eccentric setting of the cylinder 20 arranged near upper flange 50 side.Preferably, the axle center of lower flange 60 and the axle center eccentric setting of the cylinder 20 arranged near lower flange 60 side.The cylinder 20 installed in the above described manner, can ensure that cylinder 20 is fixed with the throw of eccentric of sub-rotating shaft 10 or upper flange 50, thus make piston assembly 30 have the good feature of stability of motions.
Sub-rotating shaft 10 in the utility model is slidably connected with piston assembly 30, and the volume in capacity chamber 31 changes with the rotation of sub-rotating shaft 10.Because the sub-rotating shaft 10 in the utility model and piston assembly 30 are slidably connected, thus ensure that the motion credibility of piston assembly 30, effectively avoid piston assembly 30 to move stuck problem, thus make the regular feature of volume-variation tool in capacity chamber 31.
As shown in Fig. 2, Figure 10 to Figure 13, Figure 17 to Figure 23, piston assembly 30 comprises piston sleeve 33 and at least two pistons 32, piston sleeve 33 is arranged in cylinder 20 pivotly, piston 32 is slidably arranged in form capacity chamber 31 in piston sleeve 33, and capacity chamber 31 is positioned in the glide direction of piston 32.Alternatively, the number of piston 32 is consistent with the number of cylinder 20.
In this specific embodiment, piston assembly 30 and sub-rotating shaft 10 are slidably matched, and along with the rotation of sub-rotating shaft 10, piston assembly 30 has straight line motion trend relative to sub-rotating shaft 10, thus makes rotation become the straight line motion of local.Because piston 32 and piston sleeve 33 are slidably connected, thus under the driving of sub-rotating shaft 10, effectively avoid piston 32 to move stuck, thus ensure that the motion credibility of piston 32, sub-rotating shaft 10 and piston sleeve 33, and then improve the operation stability of compressor.
In the preferred implementation shown in Fig. 1 to Figure 23, Figure 24, cylinder 20, sub-rotating shaft 10, piston 32 are respectively two, sub-rotating shaft 10 is stretched into as driving shaft in the cylinder 20 of upper flange 50 side through upper flange 50, and moves with the piston 32 in this cylinder 20 and be connected; Another sub-rotating shaft 10 is stretched in the cylinder 20 near lower flange 60 side through lower flange 60 as driven axle, and moves with the piston 32 in this cylinder 20 and be connected.Due to piston assembly 30, between cylinder 20 and sub-rotating shaft 10, form cross slides, thus make piston assembly 30 and cylinder 20 motion stabilization and continuously, and ensure that the volume-variation in capacity chamber 31 has rule, thus ensure that the operation stability of compressor, and then improve the functional reliability of heat transmission equipment.
Driving shaft is driven by motor and rotates, and driven axle drives rotation indirectly by driving shaft.
Piston 32 in the utility model has the slip hole 321 of the through setting of axis along sub-rotating shaft 10, sub-rotating shaft 10 is through slip hole 321, and the piston 32 coordinated with driving shaft rotates with driving shaft and reciprocatingly slides in piston sleeve 33 along the axial direction perpendicular to driving shaft simultaneously under the driving of driving shaft; The piston 32 coordinated with driven axle, rotates with piston sleeve 33 and drives driven axle to rotate under the driving of piston sleeve 33, and the piston 32 simultaneously coordinated with driven axle reciprocatingly slides in piston sleeve 33 along the axial direction perpendicular to driven axle.Owing to making piston 32 do straight line motion but not rotary reciprocating motion relative to sub-rotating shaft 10, thus effectively reduce eccentric mass, reduce the lateral force that sub-rotating shaft 10 and piston 32 are subject to, thus reduce the wearing and tearing of piston 32, improve the sealability of piston 32.
For above-mentioned driven axle, namely be arranged on the sub-rotating shaft 10 in the cylinder 20 of lower flange 60 side, piston sleeve 33 rotates and drives piston 32 to rotate, and the piston 32 arranged near lower flange 60 side can slide with the volume changing corresponding capacity chamber 31 in piston sleeve 33, sub-rotating shaft 10 simultaneously near lower flange 60 side is rotated under the driving effect of this piston 32, thus make piston sleeve 33 and this sub-rotating shaft 10 bear bending deflection and torsional deflection respectively, reduce the bulk deformation of single part, reduce the Structural strength calls of antithetical phrase rotating shaft 10.
Preferably, slip hole 321 is elongated hole or waist shaped hole.
Piston 32 in the utility model is in cylindricality.Preferably, the cylindrical or non-cylindrical of piston 32.
As shown in Figure 10 and Figure 11, piston 32 has symmetrically arranged a pair arcuate surface of middle vertical plane along piston 32, and arcuate surface coordinates with the internal surface adaptability of cylinder 20, and two times of the cambered surface radius of curvature of the arcuate surface internal diameters equaling cylinder 20.Like this, can make can realize Zero clearance volume in exhaust process.It should be noted that, when piston 32 is placed in piston sleeve 33, the middle vertical plane of piston 32 is the axial plane of piston sleeve 33.
The agent structure of the piston sleeve 33 in the utility model is the hollow cylinder having certain roughness to require.
In the preferred implementation shown in Figure 12 and Figure 13, there is in piston sleeve 33 pilot hole 311 of the through setting of radial direction along piston sleeve 33, pilot hole 311 is at least two, in each pilot hole 311, correspondence is provided with a piston 32, and piston 32 is slidably arranged in pilot hole 311 with linear reciprocating motion.Because piston 32 is slidably arranged in pilot hole 311, thus when piston 32 during side-to-side movement, can make the volume in capacity chamber 31 constantly change in pilot hole 311, thus ensure air-breathing, the exhaust stability of compressor.
Rotate in piston sleeve 33 to prevent piston 32, pilot hole 311 has in the orthographic projection at lower flange 60 place the straightway paralleled for a pair, the straightway paralleled for a pair is that the internal face projection that a pair of piston sleeve 33 parallels is formed, and piston 32 has the outer mold surface that the suitable and slippage of the internal face shape paralleled with a pair of pilot hole 311 coordinates.As piston 32 and the piston sleeve 33 of above-mentioned respective outer side edges, can make piston 32 in piston sleeve 33 smooth sliding and keep sealing effect.
Preferably, pilot hole 311 has a pair arcuate line segment in the orthographic projection at lower flange 60 place, and this pair arcuate line segment is connected to form irregular sectional shape with the straightway to parallel for a pair.
As shown in Figure 2, the outer circumferential face of piston sleeve 33 and the internal face shape of cylinder 20 suitable.Thus make to seal for large face between piston sleeve 33 and cylinder 20, between pilot hole 311 and piston 32, and complete machine sealing is the sealing of large face, is conducive to reducing to leak.
As shown in Figure 5, piston sleeve 33 towards the first thrust surface 332 of lower flange 60 side and the surface contact of lower flange 60.Thus piston sleeve 33 and lower flange 60 are reliably located.
As shown in Figure 12 and Figure 13, in piston sleeve 33, forming dividing plate 34 between adjacent two pilot holes 311, dividing plate 34 offering the oil-through hole 35 for being communicated with adjacent two pilot holes 311.This oil-through hole 35 is for ensureing that the sub-rotating shaft 10 of dividing plate 34 both sides can obtain the lubrication of lubricant oil smoothly.
Preferably, the axis of oil-through hole 35 parallels with the axis of sub-rotating shaft 10.
Preferably, the axis of each pilot hole 311 at least two pilot holes 311 is all parallel.
As shown in Figures 6 to 9, sub-rotating shaft 10 has the slippage section 11 be slidably matched with piston assembly 30, and slippage section 11 is positioned at one end of the close cylinder 20 of sub-rotating shaft 10, and slippage section 11 has slippage fitting surface 111.Because sub-rotating shaft 10 is slidably matched by the slip hole 321 of slippage fitting surface 111 with piston 32, thus ensure that the motion credibility of the two, effectively avoid the two stuck.
The sub-rotating shaft 10 particularly arranged near lower flange 60 side, the slippage fitting surface 111 in this sub-rotating shaft 10 coordinates with the wall surface of the hole of the slip hole 321 of corresponding piston 32, drives this sub-rotating shaft 10 to rotate to make piston 32.
Preferably, slippage section 11 has two symmetrically arranged slippage fitting surfaces 111.Because slippage fitting surface 111 is symmetrical arranged, thus make the stressed more even of two slippage fitting surfaces 111, ensure that the motion credibility of sub-rotating shaft 10 and piston 32.
As shown in Figures 6 to 9, sub-rotating shaft 10 has the slippage section 11 be slidably matched with piston assembly 30, and slippage section 11 is positioned at one end of the close cylinder 20 of sub-rotating shaft 10, and slippage section 11 has two symmetrically arranged slippage fitting surfaces 111.
Preferably, slippage fitting surface 111 parallels with the axial plane of sub-rotating shaft 10, and slippage fitting surface 111 is slidably matched on the axial direction perpendicular to sub-rotating shaft 10 with the internal face of the slip hole 321 of piston 32.
Sub-rotating shaft 10 in the utility model has oil leab 13, oil leab 13 be the internal galleries of sub-rotating shaft 10 at least partially.Due to the internal galleries at least partially of oil leab 13, thus effectively avoid lubricant oil to leak in a large number, improve the flowing reliability of lubricant oil.
As shown in Figures 6 to 9, be outside oil duct at the oil leab 13 at slippage fitting surface 111 place.Because the oil leab 13 at slippage fitting surface 111 place is outside oil duct, thus make lubricant oil can directly supply to slippage fitting surface 111 and piston 32, effectively avoid the two frictional force excessive and wear and tear, thus improve the motion smoothing of the two.
Sub-rotating shaft 10 in the utility model has oil through 14, and internal galleries is communicated with outside oil duct by oil through 14.Owing to being provided with oil through 14, thus make inside and outside oil duct to be communicated with smoothly, and also to oil leab 13 place's oiling, thus the oiling convenience of oil leab 13 can be ensure that by oil through 14 place.
Compressor in the utility model also comprises dunnage 61, dunnage 61 is arranged on the end face away from cylinder 20 side of lower flange 60, and dunnage 61 and lower flange 60 concentric arrange with supporting revolving shaft assembly, sub-rotating shaft 10 is supported in dunnage 61 through the through hole on lower flange 60, and dunnage 61 has the second thrust surface 611 for a chapelet rotating shaft 10.Owing to being provided with dunnage 61 for a chapelet rotating shaft 10, thus improve the connection reliability between each parts.
Because dunnage 61 is arranged on lower flange 60 side, thus dunnage 61 is mainly used in supporting the sub-rotating shaft 10 arranged near lower flange 60 side, to ensure its installation reliability.
As shown in figures 4 a and 4b, dunnage 61 is connected with lower flange 60 by the 4th fastening piece 82.
Preferably, the 4th fastening piece 82 is bolt or screw.
Preferably, lower flange 60 is provided with the dunnage screw hole that three confessions the 4th fastening piece 82 wears.There is bias in the barycenter of the circle that the center of four pump housing screw holes on lower flange 60 is formed and lower flange 60, its offset size is e, this amount determines the offset of the assembling of the cylinder 20 near lower flange 60 side, rotate a circle at piston sleeve 33, gas displacement V=2*2e*S, wherein S is that piston main body feature cross-section amasss; The center of dunnage screw hole and the axis coinciding of lower flange 60, coordinate fixed support plate 61 with the 4th fastening piece 82.
As shown in Figure 2, dunnage 61 is cylindrical structure, is uniformly distributed three screw holes.The end face of dunnage 61 has certain roughness requirements, with the bottom surface of the sub-rotating shaft 10 near lower flange 60 side.
As shown in Figure 1, this compressor comprises liquor separator parts 90, frame set 91, electric machine assembly 92, pump assembly 93, cover assembly 94 and lower cover and mounting plate 95, wherein, liquor separator parts 90 are arranged on the outside of frame set 91, cover assembly 94 is assemblied in the upper end of frame set 91, lower cover and mounting plate 95 are assemblied in the lower end of frame set 91, and electric machine assembly 92 and pump assembly 93 are all positioned at the inside of frame set 91, and electric machine assembly 92 is arranged on the top of pump assembly 93.The pump assembly 93 of compressor comprises above-mentioned upper flange 50, lower flange 60, cylinder 20, rotating assembly and piston assembly 30.
Preferably, above-mentioned each parts are connected by welding, hot jacket or the mode of colding pressing.
The assembly process of whole pump assembly 93 is as follows: piston 32 is arranged in pilot hole 311, cylinder 20 and piston sleeve 33 are coaxially installed simultaneously, lower flange 60 is fixed on cylinder 20, the slippage fitting surface 111 of sub-rotating shaft 10 is installed with the surface engagement paralleled for a pair of the slip hole 321 of piston 32, upper flange 50 rigid drive shaft, upper flange 50 is fixed on cylinder 20 by screw simultaneously.Thus complete the assembling of pump assembly 93, as shown in Figure 4.
Preferably, the compressor in the utility model does not arrange suction valve chip, thus effectively can reduce inhalation resistance, improves the compression efficiency of compressor.
It should be noted that, in this specific embodiment, when a piston 32 completes the motion of a week, meeting air-breathing, exhaust twice, thus make compressor have the high feature of compression efficiency.Compared with the single cylinder roller compressor of same discharge capacity, due to original first compression is divided into two second compression, the torque fluctuations of the compressor thus in the utility model is relatively little, during operation, has exhaust resistance little, effectively eliminates exhaust noise.
Specifically, as shown in Figure 17 to Figure 23, the cylinder wall of each cylinder 20 in the utility model has compressed air inlet 21 and the first compression exhaust mouth 22, when piston assembly 30 is in Inlet Position, and compressed air inlet 21 and capacity chamber 31 conducting; When piston assembly 30 is in exhaust position, capacity chamber 31 and the first compression exhaust mouth 22 conducting.
Preferably, the internal face of cylinder wall has compress inlet air dashpot 23, and compress inlet air dashpot 23 is communicated with compressed air inlet 21 (please refer to Figure 17 to Figure 23).Owing to being provided with compress inlet air dashpot 23, thus a large amount of gas can be stored at this place, to make capacity chamber 31 can full air-breathing, thus enable the enough air-breathings of compressor, and when poor inspiration, can supply in time and store gas to capacity chamber 31, to ensure the compression efficiency of compressor.
Specifically, compress inlet air dashpot 23 in the radial plane of cylinder 20 curved section, and compress inlet air dashpot 23 is extended to the first compression exhaust mouth 22 side by compressed air inlet 21, and the sense of rotation of the bearing of trend of compress inlet air dashpot 23 and piston assembly 30 in the same way.
The cylinder wall of each cylinder 20 in the utility model has the second compression exhaust mouth 24, second compression exhaust mouth 24 is between compressed air inlet 21 and the first compression exhaust mouth 22, and in the process of piston assembly 30 rotation, first all discharged by the first compression exhaust mouth 22 again after the pressure release of the second compression exhaust mouth 24 at the portion gas in piston assembly 30.Owing to being only provided with two exhaust passageways, one is be vented through the first compression exhaust mouth 22, and another is vented through the second compression exhaust mouth 24, thus decreases Leakage Gas, improve the sealing area of cylinder 20.
Preferably, compressor also comprises exhaust valve component 40, and exhaust valve component 40 is arranged on the second compression exhaust mouth 24 place.Owing to being provided with exhaust valve component 40 at the second compression exhaust mouth 24 place, thus effectively avoiding gas in capacity chamber 31 to leak in a large number, ensure that the compression efficiency in capacity chamber 31.
In the preferred implementation shown in Fig. 5, the outer wall of cylinder wall offers receiving groove 25, the bottom land of the through receiving groove 25 of the second compression exhaust mouth 24, exhaust valve component 40 is arranged in receiving groove 25.Owing to being provided with the receiving groove 25 for holding exhaust valve component 40, thus decreasing taking up room of exhaust valve component 40, parts are rationally arranged, thus improve the space availability ratio of cylinder 20.
Specifically, exhaust valve component 40 comprises exhaust valve plate 41 and valve block baffle plate 42, and exhaust valve plate 41 to be arranged in receiving groove 25 and to block the second compression exhaust mouth 24, and valve block baffle plate 42 is stacked on exhaust valve plate 41.Owing to being provided with valve block baffle plate 42, thus effectively avoiding exhaust valve plate 41 excessively to open, ensure that the exhaust performance of cylinder 20.
Preferably, exhaust valve plate 41 is connected by the first fastening piece 43 with valve block baffle plate 42.Further, the first fastening piece 43 is screws.
It should be noted that, the space outerpace of capacity chamber 31 with pump assembly 93 can separate by the exhaust valve component 40 in the utility model, for back pressure is vented: after namely when capacity chamber 31 is communicated with the second compression exhaust mouth 24, when the pressure in capacity chamber 31 is greater than space outerpace pressure (exhaust pressure), exhaust valve plate 41 is opened, and starts exhaust; If the pressure in capacity chamber 31 is still lower than exhaust pressure after being communicated with, then now exhaust valve plate 41 does not work.Now, compressor remains in operation, compression, until capacity chamber 31 is communicated with the first compression exhaust mouth 22, by the gas press-in space outerpace in capacity chamber 31, completes exhaust process.The exhaust mode of the first compression exhaust mouth 22 is forced exhaust mode.
Below the operation of compressor is specifically introduced, to rotate counterclockwise:
As shown in figure 24, the compressor in the utility model adopts cross slides principle to arrange.Wherein, the axle center O of sub-rotating shaft 10
1with the axle center O of cylinder 20
2eccentric setting, and the throw of eccentric of the two is fixed as e, and the two rotates around respective axle center respectively.Piston 32 is equivalent to the slide block in cross slides, and the axle center of piston sleeve 33 is equivalent to two connecting rod l respectively to the axle center of the distance in the axle center of piston 32 and sub-rotating shaft 10 to the distance in the axle center of piston 32
1, l
2, so just form the agent structure of crosshead shoe principle.
As shown in figure 24, when the compressor operating of said structure, sub-rotating shaft 10 is around the axle center O of sub-rotating shaft 10
1rotate; Cylinder 20 is around the axle center O of cylinder 20
2rotate, and the axle center eccentric setting of the axle center of sub-rotating shaft 10 and cylinder 20 and eccentric distance are fixed; The piston 32 of piston assembly rotates with sub-rotating shaft 10 and reciprocatingly slides in the piston sleeve 33 of piston assembly along the axial direction perpendicular to sub-rotating shaft 10 simultaneously under the driving of sub-rotating shaft 10.
As the compressor that said method runs, constitute cross slides, this operation method adopts cross slides principle, and wherein, piston 32 is as slide block, and the slippage fitting surface 111 of sub-rotating shaft 10 is as first connecting rod l
1, piston sleeve 33 pilot hole 311 as second connecting rod l
2(please refer to Figure 24).
Specifically, the axle center O of sub-rotating shaft 10
1be equivalent to first connecting rod l
1rotating center, the axle center O of cylinder 20
2be equivalent to second connecting rod l
2rotating center; The slippage fitting surface 111 of sub-rotating shaft 10 is equivalent to first connecting rod l
1, the pilot hole 311 of piston sleeve 33 is equivalent to second connecting rod l
2; Piston 32 is equivalent to slide block.Pilot hole 311 is mutually vertical with slippage fitting surface 111; Piston 32 relatively and pilot hole 311 can only to-and-fro motion, piston 32 can only to-and-fro motion relative to slippage fitting surface 111.Can find after piston 32 is reduced to barycenter, its running orbit is circular movement, and this circle is the axle center O with cylinder 20
2with the axle center O of sub-rotating shaft 10
1line be the circle of diameter.
As second connecting rod l
2when circling, slide block can along second connecting rod l
2to-and-fro motion; Meanwhile, slide block can along first connecting rod l
1to-and-fro motion.First connecting rod l
1with second connecting rod l
2remain vertical, make slide block along first connecting rod l
1vibration-direction and slide block are along second connecting rod l
2vibration-direction is mutually vertical.First connecting rod l
1with second connecting rod l
2and the relative motion relation of piston 32, form cross slides principle.
Under this movement technique, slide block circles, its angular velocity and first connecting rod l
1with second connecting rod l
2rotational velocity equal.Slide block running orbit is circle.This circle is with first connecting rod l
1rotating center and second connecting rod l
2the centre distance of rotating center be diameter.In embodiment as shown in Figure 3, two cylinders 20 differ 180 degree of interlaced arrangement.Two pistons 32 form four capacity chambeies 31 in reciprocatory movement.And the staggered 180 degree of layouts of two liquor separator parts 90 of these two cylinder 20 correspondences.Certainly, two liquor separator parts 90 also can be considered to be arranged on the same side, like this, two cylinders 20 also answer dislocation-free to arrange, and overlap completely stacked.
As shown in Figure 16 and Figure 24, wherein, differ eccentric distance e near the axle center 15 of the sub-rotating shaft of lower flange side with between piston sleeve axle center 333, piston centroid trajectory line is rounded.
Specifically, electric machine assembly 92 drives the sub-rotating shaft 10 near upper flange 50 side to rotate, the slippage fitting surface 111 of sub-rotating shaft 10 drives the piston 32 near upper flange 50 side to move, piston 32 drives piston sleeve 33 to rotate, and then drive the piston 32 near lower flange 60 side to rotate, and the sub-rotating shaft 10 near lower flange 60 side is impelled to rotate.In whole moving element, piston sleeve 33 only circles, and piston 32 1 aspect is relative to sub-rotating shaft 10 to-and-fro motion, simultaneously again relative to pilot hole 311 to-and-fro motion of piston sleeve 33, and two to-and-fro motion mutually vertically and carry out simultaneously, thus the to-and-fro motion of both direction is made to form cross slides motion mode.The compound motion of this kind cross slides makes piston 32 reciprocating relative to piston sleeve 33, and the cavity that this to-and-fro motion makes piston sleeve 33, cylinder 20 is formed with piston 32 periodically becomes greatly, reduces.And piston 32 circles relative to cylinder 20, the capacity chamber 31 that this circular movement makes piston sleeve 33, cylinder 20 and piston 32 be formed periodically is communicated with compressed air inlet 21, relief opening.Under the acting in conjunction of above two relative movement, make compressor can complete the process of air-breathing, compression, exhaust.In reciprocating process, the centroid trajectory line of piston 32 is circular, and circular diameter equals eccentric amount e, and the center of circle is on the mid point of the center of sub-rotating shaft 10 and the line of centres of piston sleeve 33.
As shown in Figure 17 to Figure 23, Figure 24, for a capacity chamber 31, when capacity chamber 31 is communicated with compressed air inlet 21, start air-breathing (please refer to Figure 17 and Figure 18); Piston sleeve 33 continues to drive piston 32, sub-rotating shaft 10 turns clockwise, and after capacity chamber 31 departs from compressed air inlet 21, whole air-breathing terminates, and now capacity chamber 31 seals completely, starts to compress (please refer to Figure 18); Continue to rotate, gas constantly compresses, and when capacity chamber 31 is communicated with the second compression exhaust mouth 24, starts to be vented (please refer to Figure 19); Continue to rotate, be constantly constantly vented while compression, until capacity chamber 31 departs from the first compression exhaust mouth 22 completely, complete whole air-breathing, compression, exhaust process (please refer to Figure 21 to Figure 23); Capacity chamber 31 connects compressed air inlet 21 after rotating to an angle again subsequently.The total displacement of compressor is V=2*2* (2e*S).
In addition, the compressor in the utility model also has Zero clearance volume, the advantage of high volumetric efficiency, effectively can also expand the discharge capacity of compressor simultaneously, and reduce the torque fluctuations of compressor.
It should be noted that used term is only to describe embodiment here, and be not intended to the illustrative embodiments of restricted root according to the application.As used herein, unless the context clearly indicates otherwise, otherwise singulative is also intended to comprise plural form, in addition, it is to be further understood that, " comprise " when using term in this manual and/or " comprising " time, it indicates existing characteristics, step, work, device, assembly and/or their combination.
It should be noted that, term " first ", " second " etc. in the specification of the application and claims and above-mentioned accompanying drawing are for distinguishing similar object, and need not be used for describing specific order or precedence.Should be appreciated that the data used like this can be exchanged in the appropriate case, so as the mode of execution of the application described herein can with except here diagram or describe those except order implement.
The foregoing is only preferred embodiment of the present utility model, be not limited to the utility model, for a person skilled in the art, the utility model can have various modifications and variations.All within spirit of the present utility model and principle, any amendment done, equivalent replacement, improvement etc., all should be included within protection domain of the present utility model.
Claims (30)
1. a compressor, is characterized in that, comprising:
Upper flange (50);
Lower flange (60);
At least two cylinders (20), described at least two cylinders (20) are folded between described upper flange (50) and described lower flange (60), and arbitrary neighborhood two described cylinders (20) work all independently of one another;
Rotating assembly, described rotating assembly is successively through described upper flange (50), described cylinder (20) and described lower flange (60), described rotating assembly comprises the sub-rotating shaft (10) arranged with each described cylinder (20) one_to_one corresponding in described at least two cylinders (20), and the axle center eccentric setting of the described cylinder (20) that the axle center of described sub-rotating shaft (10) is corresponding with rotating shaft (10) sub-described in this and eccentric distance are fixed;
Piston assembly (30), described piston assembly (30) have with each described cylinder (20) one to one capacity chamber (31), described piston assembly (30) is arranged in described cylinder (20) pivotly, and sub-rotating shaft (10) described at least one and described piston assembly (30) drive the volume being connected to change described capacity chamber (31).
2. compressor according to claim 1, is characterized in that, described piston assembly (30) comprising:
Piston sleeve (33), described piston sleeve (33) is arranged in described cylinder (20) pivotly;
At least two pistons (32), described piston (32) is slidably arranged in form described capacity chamber (31) in described piston sleeve (33), and described capacity chamber (31) is positioned in the glide direction of described piston (32).
3. compressor according to claim 2, is characterized in that, described cylinder (20), described sub-rotating shaft (10), described piston (32) are respectively two,
A described sub-rotating shaft (10) is driving shaft, stretch in the described cylinder (20) near described upper flange (50) side through described upper flange (50), and move with the described piston (32) in cylinder described in this (20) and be connected;
Sub-rotating shaft (10) described in another is driven axle, stretch in the described cylinder (20) near described lower flange (60) side through described lower flange (60), and move with the described piston (32) in cylinder described in this (20) and be connected.
4. compressor according to claim 3, is characterized in that, described driving shaft is driven by motor and rotates, and described driven axle drives rotation indirectly by described driving shaft.
5. compressor according to claim 4, it is characterized in that, described piston (32) has the slip hole (321) of the through setting of axis along described sub-rotating shaft (10), and described sub-rotating shaft (10) is through described slip hole (321)
The described piston (32) coordinated with described driving shaft rotates with described driving shaft and reciprocatingly slides in described piston sleeve (33) along the axial direction perpendicular to described driving shaft simultaneously under the driving of described driving shaft;
The described piston (32) coordinated with described driven axle, rotate with described piston sleeve (33) under the driving of described piston sleeve (33) and drive described driven axle to rotate, the described piston (32) simultaneously coordinated with described driven axle reciprocatingly slides in described piston sleeve (33) along the axial direction perpendicular to described driven axle.
6. compressor according to claim 5, is characterized in that, described slip hole (321) is elongated hole or waist shaped hole.
7. compressor according to claim 2, it is characterized in that, described piston (32) has symmetrically arranged a pair arcuate surface of middle vertical plane along described piston (32), described arcuate surface coordinates with the internal surface adaptability of described cylinder (20), and two times of the cambered surface radius of curvature of the described arcuate surface internal diameters equaling described cylinder (20).
8. compressor according to claim 2, is characterized in that, described piston (32) is in cylindricality.
9. compressor according to claim 2, it is characterized in that, there is in described piston sleeve (33) pilot hole (311) of the through setting of radial direction along described piston sleeve (33), described pilot hole (311) is at least two, the interior correspondence of each described pilot hole (311) is provided with a described piston (32), and described piston (32) is slidably arranged in described pilot hole (311) with linear reciprocating motion.
10. compressor according to claim 9, is characterized in that, the axis of each described pilot hole (311) is all parallel.
11. compressors according to claim 9, it is characterized in that, in described piston sleeve (33), forming dividing plate (34) between adjacent two described pilot holes (311), described dividing plate (34) offering the oil-through hole (35) for being communicated with adjacent two described pilot holes (311).
12. compressors according to claim 11, is characterized in that, the axis of described oil-through hole (35) parallels with the axis of described sub-rotating shaft (10).
13. compressors according to claim 9, it is characterized in that, described pilot hole (311) has in the orthographic projection at described lower flange (60) place the straightway paralleled for a pair, the described straightway paralleled for a pair is that the internal face paralleled for a pair projection of described piston sleeve (33) is formed, and described piston (32) has the outer mold surface that and slippage suitable with the described internal face shape paralleled for a pair of described pilot hole (311) coordinates.
14. compressors according to claim 2, is characterized in that, described piston sleeve (33) towards first thrust surface (332) of described lower flange (60) side and the surface contact of described lower flange (60).
15. compressors according to claim 5, it is characterized in that, described sub-rotating shaft (10) has the slippage section (11) be slidably matched with described piston assembly (30), described slippage section (11) is positioned at one end of the close described cylinder (20) of described sub-rotating shaft (10), and described slippage section (11) has slippage fitting surface (111).
16. compressors according to claim 15, is characterized in that, described slippage fitting surface (111) is symmetricly set on the both sides of described slippage section (11).
17. compressors according to claim 16, it is characterized in that, described slippage fitting surface (111) parallels with the axial plane of described sub-rotating shaft (10), and described slippage fitting surface (111) is slidably matched on the axial direction perpendicular to described sub-rotating shaft (10) with the internal face of the described slip hole (321) of described piston (32).
18. compressors according to claim 15, it is characterized in that, described sub-rotating shaft (10) has oil leab (13), and described oil leab (13) comprises and is arranged on the inner internal galleries of described sub-rotating shaft (10) and is arranged on the outside oil duct at described slippage fitting surface (111) place and is communicated with the oil through (14) of described internal galleries and described outside oil duct.
19. compressors according to claim 1, is characterized in that, adjacent two described cylinders (20) the coaxially to each other heart are arranged.
20. compressors according to claim 19, is characterized in that, the axle center of described upper flange (50) and the axle center eccentric setting of the described cylinder (20) arranged near described upper flange (50) side.
21. compressors according to claim 20, is characterized in that, the axle center of described lower flange (60) and the axle center eccentric setting of the described cylinder (20) arranged near described lower flange (60) side.
22. compressors according to any one of claim 1 to 21, it is characterized in that, described compressor also comprises dunnage (61), described dunnage (61) is arranged on the end face away from described cylinder (20) side of described lower flange (60), and described dunnage (61) and described lower flange (60) concentric arrange to support described rotating assembly, described dunnage (61) has the second thrust surface (611) for supporting described rotating assembly.
23. compressors according to claim 1, is characterized in that, the cylinder wall of each described cylinder (20) has compressed air inlet (21) and the first compression exhaust mouth (22),
When described piston assembly (30) is in Inlet Position, described compressed air inlet (21) and the conducting of described capacity chamber (31);
When described piston assembly (30) is in exhaust position, described capacity chamber (31) and described first compression exhaust mouth (22) conducting.
24. compressors according to claim 23, is characterized in that, the internal face of described cylinder wall has compress inlet air dashpot (23), and described compress inlet air dashpot (23) is communicated with described compressed air inlet (21).
25. compressors according to claim 24, it is characterized in that, described compress inlet air dashpot (23) in the radial plane of described cylinder (20) curved section, and described compress inlet air dashpot (23) is extended to described first compression exhaust mouth (22) side by described compressed air inlet (21).
26. compressors according to claim 23, it is characterized in that, the cylinder wall of each described cylinder (20) has the second compression exhaust mouth (24), described second compression exhaust mouth (24) is positioned between described compressed air inlet (21) and described first compression exhaust mouth (22), and in the process of rotating at described piston assembly (30), first all discharged by described first compression exhaust mouth (22) again after the pressure release of described second compression exhaust mouth (24) at the portion gas in described piston assembly (30).
27. compressors according to claim 26, is characterized in that, described compressor also comprises exhaust valve component (40), and described exhaust valve component (40) is arranged on described second compression exhaust mouth (24) place.
28. compressors according to claim 27, it is characterized in that, the outer wall of described cylinder wall offers receiving groove (25), the bottom land of the through described receiving groove (25) of described second compression exhaust mouth (24), described exhaust valve component (40) is arranged in described receiving groove (25).
29. compressors according to claim 28, is characterized in that, described exhaust valve component (40) comprising:
Exhaust valve plate (41), described exhaust valve plate (41) to be arranged in described receiving groove (25) and to block described second compression exhaust mouth (24);
Valve block baffle plate (42), described valve block baffle plate (42) is stacked on described exhaust valve plate (41).
30. 1 kinds of heat transmission equipments, comprise compressor, it is characterized in that, described compressor is the compressor according to any one of claim 1 to 29.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520594254.0U CN204877942U (en) | 2015-08-07 | 2015-08-07 | Compressor and indirect heating equipment |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520594254.0U CN204877942U (en) | 2015-08-07 | 2015-08-07 | Compressor and indirect heating equipment |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN204877942U true CN204877942U (en) | 2015-12-16 |
Family
ID=54822321
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201520594254.0U Active CN204877942U (en) | 2015-08-07 | 2015-08-07 | Compressor and indirect heating equipment |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN204877942U (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106065854A (en) * | 2016-07-28 | 2016-11-02 | 珠海格力节能环保制冷技术研究中心有限公司 | One turns cylinder piston compressor |
| WO2017024868A1 (en) * | 2015-08-07 | 2017-02-16 | 珠海格力节能环保制冷技术研究中心有限公司 | Fluid machinery, heat exchange device, and method for operating fluid machinery |
| WO2017024867A1 (en) * | 2015-08-07 | 2017-02-16 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor, heat exchanger, and operating method of compressor |
| CN106065860B (en) * | 2016-07-28 | 2018-08-07 | 珠海格力节能环保制冷技术研究中心有限公司 | A kind of compressor pump and compressor |
| CN109555695A (en) * | 2018-12-18 | 2019-04-02 | 珠海格力电器股份有限公司 | Piston limit structure, compressor and indirect heating equipment |
-
2015
- 2015-08-07 CN CN201520594254.0U patent/CN204877942U/en active Active
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2017024868A1 (en) * | 2015-08-07 | 2017-02-16 | 珠海格力节能环保制冷技术研究中心有限公司 | Fluid machinery, heat exchange device, and method for operating fluid machinery |
| WO2017024867A1 (en) * | 2015-08-07 | 2017-02-16 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor, heat exchanger, and operating method of compressor |
| 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 |
| CN106438356B (en) * | 2015-08-07 | 2019-01-08 | 珠海格力电器股份有限公司 | Compressor, heat exchange device and operation method of compressor |
| CN106065854A (en) * | 2016-07-28 | 2016-11-02 | 珠海格力节能环保制冷技术研究中心有限公司 | One turns cylinder piston compressor |
| CN106065854B (en) * | 2016-07-28 | 2017-11-24 | 珠海格力节能环保制冷技术研究中心有限公司 | One kind turns cylinder piston compressor |
| CN106065860B (en) * | 2016-07-28 | 2018-08-07 | 珠海格力节能环保制冷技术研究中心有限公司 | A kind of compressor pump and compressor |
| CN109555695A (en) * | 2018-12-18 | 2019-04-02 | 珠海格力电器股份有限公司 | Piston limit structure, compressor and indirect heating equipment |
| CN109555695B (en) * | 2018-12-18 | 2024-06-11 | 珠海格力电器股份有限公司 | Piston limit structure, compressor and heat exchange equipment |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN204877940U (en) | Fluid machinery and indirect heating equipment | |
| CN204877938U (en) | Fluid machinery and indirect heating equipment | |
| CN204877939U (en) | Fluid machinery and indirect heating equipment | |
| CN205064265U (en) | Fluid machinery and indirect heating equipment | |
| CN204877942U (en) | Compressor and indirect heating equipment | |
| CN204877941U (en) | Compressor and indirect heating equipment | |
| EP3333428B1 (en) | Fluid machinery, heat exchange equipment, and operating method for fluid machinery | |
| CN106438356B (en) | Compressor, heat exchange device and operation method of compressor | |
| CN106704181B (en) | Fluid machine, heat exchange device and operation method of fluid machine | |
| CN105570128A (en) | Compressor pump structure and compressor | |
| CN106704183B (en) | Fluid machine, heat exchange device and operation method of fluid machine | |
| CN105604937A (en) | Fluid machine and heat exchange device | |
| CN106438359B (en) | Compressor, heat exchange device and operation method of compressor | |
| WO2017024862A1 (en) | Fluid machine, heat exchanger, and operating method of fluid machine | |
| CN211397889U (en) | Pump body assembly, fluid machine and heat exchange equipment | |
| CN113719439A (en) | Transmission structure, transmission connection mechanism and air compressor | |
| CN205401107U (en) | Fluid machinery and indirect heating equipment | |
| CN107165822A (en) | Pump body assembly, fluid machine and heat exchange equipment | |
| CN108799108A (en) | Pump body assembly, fluid machine and heat exchange equipment | |
| CN205533217U (en) | Compressor pump body structure and compressor | |
| CN206903866U (en) | Pump body assembly, fluid machine and heat exchange equipment | |
| CN211397890U (en) | Pump body assembly, fluid machine and heat exchange equipment | |
| CN108266376B (en) | Pump body assembly, fluid machinery and heat exchange equipment | |
| CN107288881A (en) | Pump assembly, fluid machinery and heat transmission equipment | |
| KR100531282B1 (en) | Rotary compressor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant |