CN204877942U - Compressor and indirect heating equipment - Google Patents

Compressor and indirect heating equipment Download PDF

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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
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CN
China
Prior art keywords
piston
cylinder
sub
rotating shaft
compressor according
Prior art date
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Expired - Lifetime
Application number
CN201520594254.0U
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Chinese (zh)
Inventor
胡余生
杜忠诚
徐嘉
杨森
任丽萍
孔令超
张荣婷
梁社兵
邓丽颖
丁宁
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Gree Electric Appliances Inc of Zhuhai
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Zhuhai Gree Energy Saving Environmental Protection Refrigeration Technology Research Center Co Ltd
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Priority to CN201520594254.0U priority Critical patent/CN204877942U/en
Application granted granted Critical
Publication of CN204877942U publication Critical patent/CN204877942U/en
Anticipated expiration legal-status Critical
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Abstract

本实用新型提供了一种压缩机和换热设备。压缩机包括：上法兰；下法兰；至少两个气缸，至少两个气缸夹设在上法兰与下法兰之间，任意相邻两个气缸均彼此独立工作；转轴组件，转轴组件依次穿过上法兰、气缸和下法兰，转轴组件包括与至少两个气缸中的每个气缸一一对应设置的子转轴，子转轴的轴心与该子转轴对应的气缸的轴心偏心设置且偏心距离固定；活塞组件，活塞组件具有与每个气缸一一对应的变容积腔，活塞组件可枢转地设置在气缸内，且至少一个子转轴与活塞组件驱动连接以改变容积腔的容积。本实用新型中的压缩机振动小，并保证变容积腔的容积变化具有规律、减小了余隙容积，从而提高了压缩机的运行稳定性和工作可靠性。

The utility model provides a compressor and heat exchange equipment. The compressor includes: an upper flange; a lower flange; at least two cylinders, at least two cylinders are sandwiched between the upper flange and the lower flange, and any two adjacent cylinders work independently of each other; the rotating shaft assembly, the rotating shaft assembly Through the upper flange, the cylinder and the lower flange in turn, the shaft assembly includes a sub-rotation shaft corresponding to each cylinder in at least two cylinders, the axis of the sub-rotation shaft is eccentric to the axis of the cylinder corresponding to the sub-rotation shaft Set and the eccentric distance is fixed; the piston assembly, the piston assembly has a variable volume cavity corresponding to each cylinder, the piston assembly is pivotally arranged in the cylinder, and at least one sub-rotating shaft is drivingly connected to the piston assembly to change the volume of the cavity volume. The vibration of the compressor in the utility model is small, and the volume change of the variable volume cavity is guaranteed to be regular, and the clearance volume is reduced, thereby improving the operation stability and reliability of the compressor.

Description

Compressor and heat transmission equipment
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)

1.一种压缩机，其特征在于，包括：1. A compressor, characterized in that, comprising: 上法兰(50)；Upper flange (50); 下法兰(60)；lower flange (60); 至少两个气缸(20)，所述至少两个气缸(20)夹设在所述上法兰(50)与所述下法兰(60)之间，任意相邻两个所述气缸(20)均彼此独立工作；At least two cylinders (20), the at least two cylinders (20) are sandwiched between the upper flange (50) and the lower flange (60), any two adjacent cylinders (20) ) operate independently of each other; 转轴组件，所述转轴组件依次穿过所述上法兰(50)、所述气缸(20)和所述下法兰(60)，所述转轴组件包括与所述至少两个气缸(20)中的每个所述气缸(20)一一对应设置的子转轴(10)，所述子转轴(10)的轴心与该所述子转轴(10)对应的所述气缸(20)的轴心偏心设置且偏心距离固定；a rotating shaft assembly, the rotating shaft assembly passing through the upper flange (50), the cylinder (20) and the lower flange (60) in turn, the rotating shaft assembly includes the at least two cylinders (20) Each of the cylinders (20) in each of the sub-rotating shafts (10) is provided in one-to-one correspondence, and the axis of the sub-rotating shaft (10) is the axis of the cylinder (20) corresponding to the sub-rotating shaft (10). Center eccentric setting and eccentric distance fixed; 活塞组件(30)，所述活塞组件(30)具有与每个所述气缸(20)一一对应的变容积腔(31)，所述活塞组件(30)可枢转地设置在所述气缸(20)内，且至少一个所述子转轴(10)与所述活塞组件(30)驱动连接以改变所述变容积腔(31)的容积。A piston assembly (30), the piston assembly (30) has a variable volume cavity (31) corresponding to each of the cylinders (20), and the piston assembly (30) is pivotally arranged on the cylinder (20), and at least one of the sub-rotating shafts (10) is drivingly connected with the piston assembly (30) to change the volume of the variable volume chamber (31). 2.根据权利要求1所述的压缩机，其特征在于，所述活塞组件(30)包括：2. The compressor according to claim 1, characterized in that the piston assembly (30) comprises: 活塞套(33)，所述活塞套(33)可枢转地设置在所述气缸(20)内；a piston sleeve (33), the piston sleeve (33) is pivotably arranged in the cylinder (20); 至少两个活塞(32)，所述活塞(32)滑动设置在所述活塞套(33)内以形成所述变容积腔(31)，且所述变容积腔(31)位于所述活塞(32)的滑动方向上。At least two pistons (32), the pistons (32) are slidingly arranged in the piston sleeve (33) to form the variable volume chamber (31), and the variable volume chamber (31) is located in the piston ( 32) in the sliding direction. 3.根据权利要求2所述的压缩机，其特征在于，所述气缸(20)、所述子转轴(10)、所述活塞(32)各为两个，3. The compressor according to claim 2, characterized in that there are two cylinders (20), two sub shafts (10) and two pistons (32), 一个所述子转轴(10)为主动轴，穿过所述上法兰(50)伸入靠近所述上法兰(50)一侧的所述气缸(20)内，并与该所述气缸(20)内的所述活塞(32)运动连接；One of the sub-rotating shafts (10) is a drive shaft, which passes through the upper flange (50) and extends into the cylinder (20) near the upper flange (50) side, and is connected with the cylinder The piston (32) in (20) is kinematically connected; 另一个所述子转轴(10)为被动轴，穿过所述下法兰(60)伸入靠近所述下法兰(60)一侧的所述气缸(20)内，并与该所述气缸(20)内的所述活塞(32)运动连接。The other sub-rotating shaft (10) is a driven shaft, which passes through the lower flange (60) and extends into the cylinder (20) close to the side of the lower flange (60), and is connected with the said lower flange (60). Said piston (32) in the cylinder (20) is kinematically connected. 4.根据权利要求3所述的压缩机，其特征在于，所述主动轴由电机驱动旋转，所述被动轴由所述主动轴间接驱动旋转。4. The compressor according to claim 3, wherein the driving shaft is driven to rotate by a motor, and the driven shaft is indirectly driven to rotate by the driving shaft. 5.根据权利要求4所述的压缩机，其特征在于，所述活塞(32)具有沿所述子转轴(10)的轴向贯通设置的滑移孔(321)，所述子转轴(10)穿过所述滑移孔(321)，5. The compressor according to claim 4, characterized in that, the piston (32) has a sliding hole (321) provided through the axial direction of the sub-rotating shaft (10), and the sub-rotating shaft (10) ) through the slip hole (321), 与所述主动轴配合的所述活塞(32)在所述主动轴的驱动下随所述主动轴旋转并同时沿垂直于所述主动轴的轴线方向在所述活塞套(33)内往复滑动；The piston (32) cooperating with the driving shaft rotates with the driving shaft under the driving of the driving shaft and simultaneously slides reciprocally in the piston sleeve (33) along the axis direction perpendicular to the driving shaft ; 与所述被动轴配合的所述活塞(32)，在所述活塞套(33)的驱动下随所述活塞套(33)旋转并驱动所述被动轴旋转，同时与所述被动轴配合的所述活塞(32)沿垂直于所述被动轴的轴线方向在所述活塞套(33)内往复滑动。The piston (32) cooperating with the driven shaft rotates with the piston sleeve (33) under the drive of the piston sleeve (33) and drives the driven shaft to rotate, while the piston cooperating with the driven shaft The piston (32) slides reciprocally in the piston sleeve (33) in a direction perpendicular to the axis of the driven shaft. 6.根据权利要求5所述的压缩机，其特征在于，所述滑移孔(321)为长孔或腰形孔。6. The compressor according to claim 5, characterized in that, the sliding hole (321) is a long hole or a waist-shaped hole. 7.根据权利要求2所述的压缩机，其特征在于，所述活塞(32)具有沿所述活塞(32)的中垂面对称设置的一对弧形表面，所述弧形表面与所述气缸(20)的内表面适应性配合，且所述弧形表面的弧面曲率半径的二倍等于所述气缸(20)的内径。7. The compressor according to claim 2, characterized in that, the piston (32) has a pair of arc-shaped surfaces arranged symmetrically along the mid-vertical plane of the piston (32), the arc-shaped surfaces and The inner surface of the cylinder (20) is fit adaptively, and twice the arc surface curvature radius of the arc surface is equal to the inner diameter of the cylinder (20). 8.根据权利要求2所述的压缩机，其特征在于，所述活塞(32)呈柱形。8. The compressor according to claim 2, characterized in that the piston (32) is cylindrical. 9.根据权利要求2所述的压缩机，其特征在于，所述活塞套(33)中具有沿所述活塞套(33)的径向贯通设置的导向孔(311)，所述导向孔(311)为至少两个，每个所述导向孔(311)内对应设置有一个所述活塞(32)，所述活塞(32)滑动设置在所述导向孔(311)内以往复直线运动。9. The compressor according to claim 2, characterized in that, the piston sleeve (33) has a guide hole (311) penetrating in the radial direction of the piston sleeve (33), and the guide hole ( 311) is at least two, and one piston (32) is correspondingly arranged in each guide hole (311), and the piston (32) is slidably arranged in the guide hole (311) to reciprocate and linearly move. 10.根据权利要求9所述的压缩机，其特征在于，每个所述导向孔(311)的轴线均平行。10. The compressor according to claim 9, characterized in that the axes of each of the guide holes (311) are parallel. 11.根据权利要求9所述的压缩机，其特征在于，在所述活塞套(33)中相邻两个所述导向孔(311)之间形成隔板(34)，所述隔板(34)上开设有用于连通相邻两个所述导向孔(311)的过油孔(35)。11. The compressor according to claim 9, characterized in that a partition (34) is formed between two adjacent guide holes (311) in the piston sleeve (33), and the partition ( 34) is provided with an oil hole (35) for communicating with two adjacent guide holes (311). 12.根据权利要求11所述的压缩机，其特征在于，所述过油孔(35)的轴线与所述子转轴(10)的轴线相平行。12. The compressor according to claim 11, characterized in that, the axis of the oil passage hole (35) is parallel to the axis of the sub-rotating shaft (10). 13.根据权利要求9所述的压缩机，其特征在于，所述导向孔(311)在所述下法兰(60)处的正投影具有一对相平行的直线段，所述一对相平行的直线段为所述活塞套(33)的一对相平行的内壁面投影形成，所述活塞(32)具有与所述导向孔(311)的所述一对相平行的内壁面形状相适配且滑移配合的外型面。13. The compressor according to claim 9, characterized in that, the orthographic projection of the guide hole (311) at the lower flange (60) has a pair of parallel straight line segments, and the pair of opposite The parallel straight line segment is formed by the projection of a pair of parallel inner wall surfaces of the piston sleeve (33), and the piston (32) has a shape corresponding to that of the pair of parallel inner wall surfaces of the guide hole (311). Adaptive and slip-fit exterior surfaces. 14.根据权利要求2所述的压缩机，其特征在于，所述活塞套(33)的朝向所述下法兰(60)一侧的第一止推面(332)与所述下法兰(60)的表面接触。14. The compressor according to claim 2, characterized in that, the first thrust surface (332) of the piston sleeve (33) facing the side of the lower flange (60) is in contact with the lower flange (60) surface contact. 15.根据权利要求5所述的压缩机，其特征在于，所述子转轴(10)具有与所述活塞组件(30)滑动配合的滑移段(11)，所述滑移段(11)位于所述子转轴(10)的靠近所述气缸(20)的一端，且所述滑移段(11)具有滑移配合面(111)。15. The compressor according to claim 5, characterized in that, the sub-rotating shaft (10) has a sliding section (11) that is slidingly engaged with the piston assembly (30), and the sliding section (11) It is located at one end of the sub-rotating shaft (10) close to the cylinder (20), and the sliding section (11) has a sliding matching surface (111). 16.根据权利要求15所述的压缩机，其特征在于，所述滑移配合面(111)对称设置在所述滑移段(11)的两侧。16. The compressor according to claim 15, characterized in that, the sliding fitting surfaces (111) are symmetrically arranged on both sides of the sliding section (11). 17.根据权利要求16所述的压缩机，其特征在于，所述滑移配合面(111)与所述子转轴(10)的轴向平面相平行，所述滑移配合面(111)与所述活塞(32)的所述滑移孔(321)的内壁面在垂直于所述子转轴(10)的轴线方向上滑动配合。17. The compressor according to claim 16, characterized in that, the sliding fitting surface (111) is parallel to the axial plane of the sub-rotating shaft (10), and the sliding fitting surface (111) is parallel to the The inner wall surface of the sliding hole (321) of the piston (32) is slidingly fitted in a direction perpendicular to the axis of the sub-rotating shaft (10). 18.根据权利要求15所述的压缩机，其特征在于，所述子转轴(10)具有润滑油道(13)，所述润滑油道(13)包括设置在所述子转轴(10)内部的内部油道和设置在所述滑移配合面(111)处的外部油道以及连通所述内部油道和所述外部油道的通油孔(14)。18. The compressor according to claim 15, characterized in that, the sub-rotating shaft (10) has a lubricating oil passage (13), and the lubricating oil passage (13) includes The internal oil passage, the external oil passage arranged at the sliding fitting surface (111) and the oil passage hole (14) communicating the internal oil passage and the external oil passage. 19.根据权利要求1所述的压缩机，其特征在于，相邻两个所述气缸(20)彼此同轴心设置。19. The compressor according to claim 1, characterized in that, two adjacent cylinders (20) are coaxially arranged with each other. 20.根据权利要求19所述的压缩机，其特征在于，所述上法兰(50)的轴心与靠近所述上法兰(50)一侧设置的所述气缸(20)的轴心偏心设置。20. The compressor according to claim 19, characterized in that the axis of the upper flange (50) and the axis of the cylinder (20) disposed near the upper flange (50) are Eccentric setting. 21.根据权利要求20所述的压缩机，其特征在于，所述下法兰(60)的轴心与靠近所述下法兰(60)一侧设置的所述气缸(20)的轴心偏心设置。21. The compressor according to claim 20, characterized in that the axis of the lower flange (60) and the axis of the cylinder (20) disposed near the lower flange (60) are Eccentric setting. 22.根据权利要求1至21中任一项所述的压缩机，其特征在于，所述压缩机还包括支撑板(61)，所述支撑板(61)设置在所述下法兰(60)的远离所述气缸(20)一侧的端面上，且所述支撑板(61)与所述下法兰(60)同轴心设置以支撑所述转轴组件，所述支撑板(61)具有用于支撑所述转轴组件的第二止推面(611)。22. The compressor according to any one of claims 1 to 21, characterized in that, the compressor further comprises a support plate (61), and the support plate (61) is arranged on the lower flange (60 ) on the end face away from the side of the cylinder (20), and the support plate (61) is arranged concentrically with the lower flange (60) to support the shaft assembly, the support plate (61) It has a second thrust surface (611) for supporting the rotating shaft assembly. 23.根据权利要求1所述的压缩机，其特征在于，每个所述气缸(20)的气缸壁具有压缩进气口(21)和第一压缩排气口(22)，23. The compressor according to claim 1, characterized in that, the cylinder wall of each cylinder (20) has a compression intake port (21) and a first compression discharge port (22), 当所述活塞组件(30)处于进气位置时，所述压缩进气口(21)与所述变容积腔(31)导通；When the piston assembly (30) is at the air intake position, the compressed air inlet (21) is in communication with the variable volume chamber (31); 当所述活塞组件(30)处于排气位置时，所述变容积腔(31)与所述第一压缩排气口(22)导通。When the piston assembly (30) is in the exhaust position, the variable volume chamber (31) communicates with the first compression exhaust port (22). 24.根据权利要求23所述的压缩机，其特征在于，所述气缸壁的内壁面具有压缩进气缓冲槽(23)，所述压缩进气缓冲槽(23)与所述压缩进气口(21)连通。24. The compressor according to claim 23, characterized in that, the inner wall surface of the cylinder wall has a compression intake buffer groove (23), and the compression intake buffer groove (23) is connected to the compression intake port (21) CONNECTED. 25.根据权利要求24所述的压缩机，其特征在于，所述压缩进气缓冲槽(23)在所述气缸(20)的径向平面内呈弧形段，且所述压缩进气缓冲槽(23)由所述压缩进气口(21)处向所述第一压缩排气口(22)所在一侧延伸。25. The compressor according to claim 24, characterized in that, the compressed air intake buffer groove (23) is an arc segment in the radial plane of the cylinder (20), and the compressed intake air buffer The groove (23) extends from the compression air inlet (21) to the side where the first compression air outlet (22) is located. 26.根据权利要求23所述的压缩机，其特征在于，每个所述气缸(20)的气缸壁具有第二压缩排气口(24)，所述第二压缩排气口(24)位于所述压缩进气口(21)与所述第一压缩排气口(22)之间，且在所述活塞组件(30)转动的过程中，在所述活塞组件(30)内的部分气体先经过所述第二压缩排气口(24)的泄压后再由所述第一压缩排气口(22)全部排出。26. The compressor according to claim 23, characterized in that, the cylinder wall of each cylinder (20) has a second compression exhaust port (24), and the second compression exhaust port (24) is located at Between the compressed air inlet (21) and the first compressed exhaust port (22), and during the rotation of the piston assembly (30), part of the gas in the piston assembly (30) After the pressure relief of the second compression exhaust port (24), it is completely discharged from the first compression exhaust port (22). 27.根据权利要求26所述的压缩机，其特征在于，所述压缩机还包括排气阀组件(40)，所述排气阀组件(40)设置在所述第二压缩排气口(24)处。27. The compressor according to claim 26, characterized in that, the compressor further comprises a discharge valve assembly (40), and the discharge valve assembly (40) is arranged at the second compression discharge port ( 24) Department. 28.根据权利要求27所述的压缩机，其特征在于，所述气缸壁的外壁上开设有容纳槽(25)，所述第二压缩排气口(24)贯通所述容纳槽(25)的槽底，所述排气阀组件(40)设置在所述容纳槽(25)内。28. The compressor according to claim 27, characterized in that, an accommodation groove (25) is opened on the outer wall of the cylinder wall, and the second compression exhaust port (24) passes through the accommodation groove (25) The bottom of the groove, the exhaust valve assembly (40) is arranged in the containing groove (25). 29.根据权利要求28所述的压缩机，其特征在于，所述排气阀组件(40)包括：29. The compressor according to claim 28, wherein the discharge valve assembly (40) comprises: 排气阀片(41)，所述排气阀片(41)设置在所述容纳槽(25)内并遮挡所述第二压缩排气口(24)；an exhaust valve plate (41), the exhaust valve plate (41) is arranged in the accommodation groove (25) and blocks the second compression exhaust port (24); 阀片挡板(42)，所述阀片挡板(42)叠置在所述排气阀片(41)上。A valve plate baffle (42), the valve plate baffle (42) is stacked on the exhaust valve plate (41). 30.一种换热设备，包括压缩机，其特征在于，所述压缩机是权利要求1至29中任一项所述的压缩机。30. A heat exchange device, comprising a compressor, characterized in that the compressor is the compressor according to any one of claims 1-29.
CN201520594254.0U 2015-08-07 2015-08-07 Compressor and indirect heating equipment Expired - Lifetime CN204877942U (en)

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Cited By (7)

* Cited by examiner, † Cited by third party
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
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
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
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 heat exchange equipment
CN116241467A (en) * 2021-12-07 2023-06-09 珠海格力电器股份有限公司 Fluid machinery and heat exchange equipment with bearings
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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
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
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
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
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
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
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 heat exchange equipment
CN109555695B (en) * 2018-12-18 2024-06-11 珠海格力电器股份有限公司 Piston limiting structure, compressor and heat exchange equipment
CN116241467A (en) * 2021-12-07 2023-06-09 珠海格力电器股份有限公司 Fluid machinery and heat exchange equipment with bearings
CN116241465A (en) * 2021-12-07 2023-06-09 珠海格力电器股份有限公司 Fluid machinery, heat exchange equipment and operating method of fluid machinery
CN116241465B (en) * 2021-12-07 2025-11-07 珠海格力电器股份有限公司 Fluid machine, heat exchange device and method for operating a fluid machine
CN116241467B (en) * 2021-12-07 2025-11-11 珠海格力电器股份有限公司 Fluid machine and heat exchange device with bearing

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