CN103206455B - Motor front bearing and centrifugal compressor and refrigeration equipment comprising same - Google Patents
Motor front bearing and centrifugal compressor and refrigeration equipment comprising same Download PDFInfo
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- CN103206455B CN103206455B CN201210015294.6A CN201210015294A CN103206455B CN 103206455 B CN103206455 B CN 103206455B CN 201210015294 A CN201210015294 A CN 201210015294A CN 103206455 B CN103206455 B CN 103206455B
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- 238000005057 refrigeration Methods 0.000 title abstract 2
- 239000000446 fuel Substances 0.000 claims description 39
- 238000004804 winding Methods 0.000 claims description 3
- 238000005461 lubrication Methods 0.000 abstract description 8
- 239000003921 oil Substances 0.000 description 329
- 239000000314 lubricant Substances 0.000 description 39
- 238000000034 method Methods 0.000 description 10
- 238000010586 diagram Methods 0.000 description 9
- 230000000694 effects Effects 0.000 description 9
- 230000008569 process Effects 0.000 description 6
- 230000015572 biosynthetic process Effects 0.000 description 4
- 230000001050 lubricating effect Effects 0.000 description 4
- 239000000463 material Substances 0.000 description 4
- 230000009471 action Effects 0.000 description 3
- 238000001816 cooling Methods 0.000 description 3
- 238000005299 abrasion Methods 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 230000013011 mating Effects 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 238000012384 transportation and delivery Methods 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 150000001875 compounds Chemical class 0.000 description 1
- 230000004069 differentiation Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
- 230000003094 perturbing effect Effects 0.000 description 1
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Abstract
The invention provides a motor front bearing, a centrifugal compressor comprising the motor front bearing and refrigeration equipment comprising the motor front bearing. The motor front bearing comprises a front bearing bush (11) and a front bearing bush positioning piece (12), wherein a front bearing main oil supply channel (121) is arranged on the front bearing bush positioning piece (12) along the radial direction, the front bearing bush (11) comprises a front bearing radial oil supply channel (112) which penetrates through the front bearing bush (11) along the radial direction and a front bearing circumferential oil supply groove (115) which is arranged at the outlet position of the front bearing radial oil supply channel (112), and the front bearing radial oil supply channel (112) comprises a front bearing lateral oil supply channel which stretches out along the lateral direction and extends to the end parts of the two ends of the front bearing bush (11). According to the motor front bearing, the bearing oil supply mode can be improved, the temperature fields of the radial bearing and the thrust bearing are uniform, the dynamic pressure state of an oil film on a thrust surface is stabilized, and the stability of oil film lubrication is improved.
Description
Technical field
The present invention relates to filed of air conditioning, in particular to a kind of motor fore bearing and the centrifugal compressor that comprises this bearing, chiller plant.
Background technique
In direct connection frequency conversion centrifugal compressor, owing to cancelling gear up structure, all axial forces, radial force act on motor front and back two bearings entirely, and bearing bears load with respect to much bigger with the bearing load of gear up structure.Therefore, the fuel feeding of bearing, lubricated seem more important.
The sliding bearing of conventional centrifugal compressor adopts circumferential fuel feeding or axial fuel system, by the main oil supply in centre to two ends fuel feeding, for the bearing with thrust structure, lubricant oil often enters thrust structure after radial component again, tend to like this cause that to enter the oil temperature of thrust face very high, by the temperature rise of thrust face, oil temperature probably exceedes the temperature of bush material permission and lost efficacy in addition; In addition, owing to entering, oil temperature in thrust face is too high, causes lubricating oil viscosity to decline, and oily film formed kinetic pressure declines, and does not reach design point requirement, finally because oil film dynamic pressure causes bearing bush abrasion not.
Obviously, if still adopt the fuel system of conventional bearing in direct connection frequency conversion centrifugal compressor, be not all right, therefore, need to find a kind of bearing structure of the operating conditions that is more applicable to direct connection frequency-changeable compressor high speed, heavy duty.
Summary of the invention
The present invention aims to provide a kind of motor fore bearing and the centrifugal compressor that comprises this bearing, chiller plant, can improve bearing fuel system, evenly radial bearing, thrust bearing temperature field, and steady propulsion face oil film dynamic pressure state, improves the stability of film lubrication.
To achieve these goals, according to an aspect of the present invention, a kind of motor fore bearing is provided, comprise fore bearing bearing shell and be set in the fore bearing bearing shell locating piece outside fore bearing bearing shell, fore bearing bearing shell locating piece is radially provided with the main oil supply gallery of fore bearing, on fore bearing bearing shell, comprise radially oil supply gallery and be arranged on the radially circumferential oil supply of fore bearing of the exit position of oil supply gallery of fore bearing of the fore bearing that is connected with the main oil supply gallery of fore bearing and radially run through fore bearing bearing shell, fore bearing radially comprises along the fore bearing side direction oil supply gallery that extends laterally and extend to end, fore bearing bearing shell two ends on oil supply gallery.
Further, fore bearing radially oil supply gallery is positioned at the middle part of fore bearing bearing shell, fore bearing side direction oil supply gallery comprises fore bearing the first side direction oil supply gallery and fore bearing the second side direction oil supply gallery, fore bearing the first side direction oil supply gallery extends to the first end end of fore bearing bearing shell, and fore bearing the second side direction oil supply gallery extends to the second end end of fore bearing bearing shell.
Further, fore bearing the first side direction oil supply gallery and fore bearing the second side direction oil supply gallery are along the axial direction horizontal-extending of fore bearing bearing shell, and the sectional area of fore bearing the second side direction oil supply gallery is greater than the sectional area of fore bearing the first side direction oil supply gallery.
Further, fore bearing the first side direction oil supply gallery and fore bearing the second side direction oil supply gallery are obliquely extended to respectively the end of fore bearing bearing shell, and the sectional area of fore bearing the second side direction oil supply gallery is greater than the sectional area of fore bearing the first side direction oil supply gallery.
Further, the first end end that is provided with the past bearing bush on the inwall of fore bearing bearing shell is in axial direction through to the axial oil supply of fore bearing of the second end end of fore bearing bearing shell, fore bearing the first side direction oil supply gallery is connected with the axial oil supply of fore bearing in the first end end of fore bearing bearing shell, and fore bearing the second side direction oil supply gallery is connected with the axial oil supply of fore bearing in the second end end of fore bearing bearing shell.
Further, the fore bearing radially entry position of oil supply gallery is provided with the fore bearing that is connected with the main oil supply gallery of fore bearing fuel feeding distributing chute in parallel, fore bearing the first side direction oil supply gallery and fore bearing the second side direction oil supply gallery fore bearing fuel feeding distributing chute place in parallel and fore bearing radially oil supply gallery be arranged in parallel.
Further, fore bearing the first side direction oil supply gallery, fore bearing the second side direction oil supply gallery and fore bearing radially the flow area sum of oil supply gallery be less than or equal to the flow area of fore bearing fuel feeding distributing chute in parallel.
Further, fore bearing bearing shell comprises radially oil supply gallery of multiple fore bearings, and multiple fore bearings radially oil supply gallery evenly arrange along the circumferential direction of fore bearing bearing shell.
Further, fore bearing fuel feeding distributing chute in parallel along circumferential direction winding on the outer wall of fore bearing bearing shell.
Further, fore bearing the first side direction oil supply gallery comprises with the fore bearing dispensing section that radially oil supply gallery is connected and is connected and extends to the extending section of the first end end of fore bearing bearing shell with dispensing section, and the sectional area of extending section is greater than the sectional area of dispensing section.
According to a further aspect in the invention, provide a kind of centrifugal compressor, comprised motor fore bearing, this motor fore bearing is above-mentioned motor fore bearing.
In accordance with a further aspect of the present invention, provide a kind of chiller plant, comprised centrifugal compressor, this centrifugal compressor is above-mentioned centrifugal compressor.
Apply technological scheme of the present invention, motor fore bearing comprises fore bearing bearing shell and is set in the fore bearing bearing shell locating piece outside fore bearing bearing shell, fore bearing bearing shell locating piece is radially provided with the main oil supply gallery of fore bearing, on fore bearing bearing shell, comprise radially oil supply gallery and be arranged on the radially circumferential oil supply of fore bearing of the exit position of oil supply gallery of fore bearing of the fore bearing that is connected with the main oil supply gallery of fore bearing and radially run through fore bearing bearing shell, fore bearing radially comprises along the fore bearing side direction oil supply gallery that extends laterally and extend to end, fore bearing bearing shell two ends on oil supply gallery.Because there is load-carrying surface at the two ends of motor fore bearing, therefore, need on fore bearing, process radially and the two ends oil supply gallery of totally three directions.The oil supply gallery of three directions is arranged in parallel, radially oil supply gallery is for meeting the lubricated needs of the radial load between rotor and fore bearing for fore bearing, and two fore bearing side direction oil supply galleries are respectively used to meet the lubricated needs between fore bearing two ends and rotor thrust face.In fore bearing working procedure, due to lubricant oil can be respectively by fore bearing side direction oil supply gallery and fore bearing radially oil supply gallery be lubricated and lower the temperature, therefore, the lubricant oil that flows to the axial load-carrying surface of fore bearing can not cause that to enter the oil temperature of thrust face too high owing to first entering thrust structure after axial component again, exceed the temperature of bush material permission and lost efficacy, can not affect lubricant oil and form dynamic pressure oil film, thereby improve motor rear bearing reliability of operation yet.
Fore bearing the first side direction oil supply gallery and fore bearing the second side direction oil supply gallery are obliquely extended to respectively the end of fore bearing bearing shell, and the sectional area of fore bearing the second side direction oil supply gallery is greater than the sectional area of fore bearing the first side direction oil supply gallery.The axial force that the bearing shaft being communicated with due to fore bearing the second side direction oil supply gallery is born to load-carrying surface is larger, therefore, make the sectional area of fore bearing the second side direction oil supply gallery be greater than the sectional area of fore bearing the first side direction oil supply gallery, when lubricant oil divides timing, can suitably distribute according to the sectional area of oil supply gallery, thereby guarantee that lubricant oil has better lubricated and cooling-down effect.
Accompanying drawing explanation
The accompanying drawing that forms a part of the present invention is used to provide a further understanding of the present invention, and schematic description and description of the present invention is used for explaining the present invention, does not form inappropriate limitation of the present invention.In the accompanying drawings:
Fig. 1 shows the oil supply structure schematic diagram of the motor fore bearing of centrifugal compressor according to an embodiment of the invention;
Fig. 2 shows according to the structure for amplifying schematic diagram at the L place of the motor fore bearing of the centrifugal compressor of Fig. 1;
Fig. 3 shows the oil supply structure schematic diagram of the motor rear bearing of centrifugal compressor according to an embodiment of the invention;
Fig. 4 shows according to the structure for amplifying schematic diagram at the M place of the motor rear bearing of the centrifugal compressor of Fig. 3;
Fig. 5 shows the sectional structure schematic diagram of the fore bearing bearing shell of the motor fore bearing of centrifugal compressor according to an embodiment of the invention;
Fig. 6 shows the perspective view of the fore bearing bearing shell of the motor fore bearing of centrifugal compressor according to an embodiment of the invention;
Fig. 7 shows the sectional structure schematic diagram of the rear bearing bearing shell of the motor rear bearing of centrifugal compressor according to an embodiment of the invention;
Fig. 8 shows the perspective view of the rear bearing bearing shell of the motor rear bearing of centrifugal compressor according to an embodiment of the invention;
Fig. 9 shows the structural representation of the rotor thrust face of centrifugal compressor according to an embodiment of the invention;
Figure 10 show according to the G-G of the rotor thrust face of the centrifugal compressor of Fig. 9 to sectional structure schematic diagram;
Figure 11 show according to the H-H of the rotor thrust face of the centrifugal compressor of Fig. 9 to sectional structure schematic diagram;
Figure 12 show according to the I-I of the rotor thrust face of the centrifugal compressor of Fig. 9 to sectional structure schematic diagram;
Figure 13 shows the structural representation of the thrust disc thrust face of centrifugal compressor according to an embodiment of the invention; And
Figure 14 show according to the K-K of the thrust disc thrust face of the centrifugal compressor of Figure 13 to broken section structural representation.
Embodiment
Hereinafter with reference to accompanying drawing, also describe the present invention in detail in conjunction with the embodiments.It should be noted that, in the situation that not conflicting, the feature in embodiment and embodiment in the application can combine mutually.
As shown in Figures 1 to 6, according to embodiments of the invention, motor fore bearing 10 (hereinafter to be referred as fore bearing) comprises fore bearing bearing shell 11 and is set in the fore bearing bearing shell locating piece 12 outside fore bearing bearing shell 11, fore bearing bearing shell locating piece 12 is fixedly installed, and fore bearing bearing shell 11 is formed to positioning action.
Fore bearing 10 is processed as split type structure, and to be assemblied in rotor 30 rear with pin location, the cylindricity that keeps two-part bearing to coordinate, is then tightened by bolts.When fore bearing bearing shell 11 is installed, fore bearing 10 is set on rotor 30, make fore bearing 10 and rotor 30 be assembled into assembly, the assembly then fore bearing bearing shell 11 and rotor 30 being assembled into is installed and is positioned in fore bearing bearing shell locating piece 12 by bearing assemble face.Fore bearing bearing shell locating piece 12 closely cooperates with fore bearing bearing shell 11, prevents that fore bearing bearing shell 11 from following rotor journal and rotating together.On bearing assemble face, be provided with seal groove, in seal groove, be provided with Sealing, the seal makes to form sealing between fore bearing bearing shell 11 and fore bearing bearing shell locating piece 12, prevents that lubricant oil from leaking along the matching gap of fore bearing bearing shell 11 and fore bearing bearing shell locating piece 12.After the relative position between fixing fore bearing bearing shell 11, rotor 30 and fore bearing bearing shell locating piece 12, the fore bearing bearing shell 11 of fore bearing 10 and fore bearing bearing shell locating piece 12 are locked with bolt.
Fore bearing bearing shell locating piece 12 comprises the main oil supply gallery 121 of fore bearing arranging along fore bearing radial direction, the first end of the main oil supply gallery 121 of fore bearing is communicated to bearing shell, the second end of the main oil supply gallery 121 of fore bearing is communicated to oil sources, thereby lubricant oil is introduced, the interior participation of fore bearing 10 is lubricated and cooling.
Fore bearing bearing shell 11 comprises on the bearing assemble face that is arranged on fore bearing bearing shell 11, and the fuel feeding distributing chute 111 in parallel being connected mutually with the main oil supply gallery 121 of fore bearing on fore bearing bearing shell locating piece 12.Fuel feeding distributing chute 111 in parallel along the circumferential direction winding of the bearing assemble face (being the external cylindrical surface coordinating with fore bearing bearing shell locating piece 12 of fore bearing bearing shell 11) of fore bearing bearing shell 11 on the outer wall of fore bearing bearing shell 11.
Fore bearing bearing shell 11 also comprises radially oil supply gallery 112 and the fore bearing side direction oil supply gallery of fore bearing being connected with fuel feeding distributing chute 111 in parallel.Fore bearing radially oil supply gallery 112 is positioned at the medium position of the axial direction of fore bearing bearing shell 10, along the radial direction of fore bearing bearing shell 11, runs through fore bearing bearing shell 11.At fore bearing, be radially provided with the circumferential oil supply 115 of fore bearing in the exit position of oil supply gallery 112.The circumferential oil supply 115 of fore bearing circumferentially arranges and forms annular oil supply along the inwall of fore bearing bearing shell 11.The first end end that includes the past bearing bush 11 on the inwall of fore bearing bearing shell 11 is in axial direction through to the axial oil supply 116 of fore bearing of the second end end of fore bearing bearing shell 11, the axial oil supply 116 of fore bearing runs through the circumferential oil supply 115 of fore bearing, lubricant oil enters after the circumferential oil supply 115 of fore bearing, by the axial oil supply 116 of fore bearing, enter the mating part of rotor 30 and fore bearing bearing shell 11, and form dynamic pressure oil film between rotor 30 and fore bearing bearing shell 11, avoid rotor 30 to contact with the direct of fore bearing bearing shell 11, fore bearing bearing shell 11 is formed to effectively protection.
Fore bearing side direction oil supply gallery comprises fore bearing the first side direction oil supply gallery 113 and fore bearing the second side direction oil supply gallery 114.Fore bearing the first side direction oil supply gallery 113 and fore bearing the second side direction oil supply gallery 114 are separately positioned on the radially both sides of oil supply gallery 112 of fore bearing, with fore bearing radially oil supply gallery 112 be arranged in parallel.Fore bearing the first side direction oil supply gallery 113 and fore bearing the second side direction oil supply gallery 114 are from fuel feeding distributing chute in parallel 111s, fore bearing the first side direction oil supply gallery 113 is obliquely extended to the first end end of fore bearing bearing shell 11, and fore bearing the second side direction oil supply gallery 114 is obliquely extended to the second end end of fore bearing bearing shell 11.
In the middle of the present embodiment, fore bearing the first side direction oil supply gallery 113 is connected with the axial oil supply 116 of fore bearing in the first end end of fore bearing bearing shell 11, and fore bearing the second side direction oil supply gallery 114 is connected with the axial oil supply 116 of fore bearing in the second end end of fore bearing bearing shell 11.At the end cohesive position of fore bearing the first side direction oil supply gallery 113 and fore bearing the second side direction oil supply gallery 114 and fore bearing bearing shell 11, all along the axial direction of the inwall of fore bearing bearing shell 11, be provided with first and cross oil groove 117, on rotor 30, include circumferential setting and cross with first point oil groove 36 that oil groove 117 coordinates.
For motor fore bearing 10, because there is load-carrying surface both sides, therefore, fore bearing 10 is processed to the oil supply gallery of three directions, and oil supply gallery is all come together in fore bearing fuel feeding distributing chute 111 in parallel.Consider that rotor 30 is when operation, the bearing load difference of 10 3 directions of fore bearing, therefore, need be optimized design to the oil supply gallery of three directions, many group oil supply galleries is set so that mean allocation fuel feeding oil mass.For make radially or axially fuel feeding distribute more even, as: for radially, can be on fore bearing circumference the multiple radially oil supply holes of mean allocation, quantity is 1～6 (being also the quantity of the oil supply gallery in parallel on each thrust face).Correspondingly, for the axial direction of fore bearing bearing shell 10, also process corresponding axially oil supply gallery.Specifically with regard to the fore bearing of single group oil supply gallery is set, need meet fore bearing the first side direction oil supply gallery 113, fore bearing the second side direction oil supply gallery 114 and fore bearing radially the flow area of oil supply gallery 112 be less than or equal to the flow area of fuel feeding distributing chute 111 in parallel with fore bearing.For single group oil supply gallery, its physical dimension feature is as follows: auxiliary side-thrust face oil supply hole d1: φ 1.5～φ 3.5mm, master thrust face oil supply hole d2: φ 4.5～φ 7.5mm, radial bearing surface oil supply hole d3: φ 4.5～φ 7.5mm, fuel feeding distributing chute width w1:10～15mm in parallel, fuel feeding distributing chute height h1:4～8mm in parallel.If many group oil supply galleries are set, for guaranteeing that many group oil supply gallery fuel deliveries are set and only arranging that single to organize fuel delivery in oil supply gallery situation consistent, should guarantee that multiple radially oil supply gallery flow area sums of arranging equate with the flow area that single radially oil supply gallery while organizing oil supply gallery is only set, and the setting of side direction oil supply gallery is also like this, when single group oil supply gallery is even only set, radially oil supply gallery, the first side direction oil supply gallery, the circulation area of the second side direction oil supply gallery is respectively A, B, C, in the time of while being provided with N group oil supply gallery, every group of circulation area corresponding to oil supply gallery is respectively a, b, c, need to meet following equation:
A+B+C=N (a+b+c), and A=Na, B=Nb, C=Nc
Take the view shown in Fig. 1 as example, the bearing producing due to impeller High Rotation Speed left, therefore the Main thrust face of fore bearing is on right side, simultaneously in order to prevent impeller reversing and to reduce perturbing of rotor cantilever segment, left side also arranges thrust face, and therefore whole fore bearing has been concentrated Main thrust face and two kinds of forms of auxiliary thrust face.Due to two thrust face stressing conditions differences, required oil mass is also different, therefore, and fuel feeding aperture difference.Right side is Main thrust face, therefore, the sectional area of fore bearing the second side direction oil supply gallery 114 extending to the right along the axial direction of fore bearing bearing shell 11 is greater than the sectional area of fore bearing the first side direction oil supply gallery 113 extending to the left along the axial direction of fore bearing bearing shell 11, to make more lubricant oil can enter right side thrust face, participate in lubricated and cooling, obviously, the structure that this differentiation arranges is more reasonable.
Incorporated by reference to shown in Figure 2, fore bearing the first side direction oil supply gallery 113 that is positioned at left side in this figure consists of the different two-part in aperture, comprise with the fore bearing dispensing section 118 that radially oil supply gallery 112 is connected and be connected and extend to the extending section 119 of the first end end of fore bearing bearing shell 11 with dispensing section 118, the sectional area of extending section 119 is greater than the sectional area of dispensing section 118.So arranging is in order to change fuel feeding flow velocity, to the flow velocity of lubricant oil in fore bearing the first side direction oil supply gallery 113 mated with the stressed of rotor thrust face 34.
On two rotor thrust faces 34, be provided with and hold oil groove 31, this holds oil groove 31 and first on fore bearing bearing shell 11 crosses oil groove 117 and is connected, and in the process of rotating at rotor, first crosses lubricant oil in oil groove 117 under the effect of rotor centrifugal force, enter and hold in oil groove 31, and accumulate.First crosses the circumferential direction setting of oil groove 117 along fore bearing bearing shell 11, lubricant oil enter first cross oil groove 117 interior after, can cross oil groove 117 along first is circumferentially uniformly distributed, thereby pass through first, cross oil groove 117 uniform-flows between the axial load-carrying surface of each thrust face and fore bearing, form good lubrication effect.
In the middle of other embodiment, fore bearing the first side direction oil supply gallery 113 and fore bearing the second side direction oil supply gallery 114 also in the past the fore bearing of bearing bush 11 radially the middle part of oil supply gallery 112 is along the axial direction horizontal-extending of fore bearing bearing shell 11, and the sectional area of fore bearing the second side direction oil supply gallery 114 is greater than the sectional area of fore bearing the first side direction oil supply gallery 113.The main oil supply gallery 121 of fore bearing in lubricant oil the past bearing bush locating piece 12 flows into, enter fore bearing radially in oil supply gallery 112, and be divided into three strands, one flows to the first end end face of fore bearing bearing shell 11, lubricating between the first end end face of participation fore bearing bearing shell 11 and rotor thrust face 34; One flows to the second end end face of fore bearing bearing shell 11, lubricating between the second end end face of participation fore bearing bearing shell 11 and rotor thrust face 34; One flows to the circumferential oil supply 115 of fore bearing of fore bearing bearing shell 11, participates in lubricating between rotor 30 and the inwall of fore bearing bearing shell 11.
Incorporated by reference to referring to shown in Fig. 1 to Fig. 4, according to embodiments of the invention, centrifugal compressor comprises rotor 30 and bearing unit, and bearing unit is set on rotor 30.Bearing unit had both comprised radially load-carrying surface, also comprised axial load-carrying surface, and like this, this bearing unit plays compound action, and radial load that can bear rotor 30, also can bear axial load, and compact structure.Rotor 30 comprises the thrust face matching with the axial load-carrying surface of bearing unit, on at least one thrust face of rotor 30, be provided with and hold oil groove 31, the oil supply gallery holding in the axial load-carrying surface of oil groove 31 and bearing unit is connected, and in the process of bearing unit work, accumulates lubricant oil.
When centrifugal compressor meets accident and stops operating; the lubricant oil being accumulated in oil groove 31 can discharge; participate in lubricating between bearing unit and rotor 30; thereby the bearing shell of bearing unit is formed to protection; thereby can prevent from, owing to lacking the lubricated too high tile kilning phenomenon that causes of bearing bush temperature that causes, improving the reliability of compressor operating.
Bearing unit comprises above-mentioned motor fore bearing 10 and motor rear bearing 20 (hereinafter to be referred as rear bearing), and the first end of rear bearing 20 is outside equipped with thrust disc 33, and thrust disc 33 is bolted and is arranged on rotor 30.Thrust face comprises the rotor thrust face 34 coordinating with fore bearing 10 and the thrust disc thrust face 35 coordinating with rear bearing, and fore bearing 10 is arranged between two rotor thrust faces 34 of rotor 30.
Incorporated by reference to referring to shown in Fig. 3, Fig. 4, Fig. 7 and Fig. 8, rear bearing 20 comprises rear bearing bearing shell 21 and rear bearing bearing shell locating piece 22.Rear bearing bearing shell locating piece 22 is fixedly installed, and rear bearing bearing shell 21 is formed to positioning supports effect.Rear bearing bearing shell 21 is set on rotor 30, and the first end outside of rear bearing bearing shell 21 is fixedly installed thrust disc 33.Thrust disc 33 is bolted to connection on rotor 30, and rear bearing bearing shell 21 is formed to axial force.
Rear bearing bearing shell locating piece 22 comprises rear bearing fuel feeding distributing chute 221 in parallel and the main oil supply gallery 222 of rear bearing.Rear bearing fuel feeding distributing chute 221 in parallel is arranged on the inwall of rear bearing bearing shell locating piece 22 along circumferential direction, forms circumferential oil supply gallery.The main oil supply gallery 222 of rear bearing is along the radial direction setting of rear bearing bearing shell locating piece 22, and is communicated with rear bearing fuel feeding distributing chute 221 in parallel, for lubricant oil being delivered to rear bearing fuel feeding distributing chute 221 in parallel, distributes.
Rear bearing bearing shell 21 comprises radially oil supply gallery 211, the circumferential oil supply 212 of rear bearing, rear bearing side direction oil supply gallery and the axial oil supply 213 of rear bearing of rear bearing.Rear bearing radially oil supply gallery 211 is arranged on the neutral position of rear bearing bearing shell 21 axial directions, along the radial direction setting of rear bearing bearing shell 21, and runs through the sidewall of rear bearing bearing shell 21.The circumferential oil supply 212 of rear bearing is arranged on the radially exit position of oil supply gallery 211 of rear bearing along the circumferential direction of the inwall of rear bearing bearing shell 21, and lubricant oil is radially introduced to inwall from the outer wall of rear bearing bearing shell 21.The axial oil supply 213 of rear bearing is in axial direction arranged on the inwall of rear bearing bearing shell 21, along the first end of rear bearing bearing shell 21, extend to the second end of rear bearing bearing shell 21, and be connected with the circumferential oil supply 212 of rear bearing, the lubricant oil entering in the circumferential oil supply 212 of rear bearing is in axial direction distributed between rotor 30 and rear bearing bearing shell 21, to form dynamic pressure oil film between rotor 30 and rear bearing bearing shell 21.
One end of rear bearing side direction oil supply gallery is communicated with rear bearing fuel feeding distributing chute 221 in parallel, and the other end extends to the first end endface position of rear bearing bearing shell 21.Rear bearing side direction oil supply gallery is arranged between rear bearing fuel feeding distributing chute 221 in parallel and the axial oil supply 213 of rear bearing.Rear bearing side direction oil supply gallery comprises rear bearing the first side direction oil supply gallery 214 and rear bearing the second side direction oil supply gallery 215.Rear bearing the first side direction oil supply gallery 214 from rear bearing radially oil supply gallery 211 extend to the first end end face of rear bearing bearing shell 21, by lubricant oil from rear bearing radially oil supply gallery 211 introduce between the axial load-carrying surface of rear bearing 20 and the thrust disc thrust face 35 of rotor 30.
Rear bearing bearing shell 21 also comprises and being communicated with rear bearing fuel feeding distributing chute 221 in parallel and along the heavy oilhole 216 radially extending of rear bearing bearing shell 21, heavy oilhole 216 is blind hole, and rear bearing the second side direction oil supply gallery 215 extends laterally to the first end end of rear bearing bearing shell 21 from the end of heavy oilhole 216.
Rear bearing the first side direction oil supply gallery 214 and rear bearing the second side direction oil supply gallery 215 can obliquely arrange, also can be horizontally disposed with along the axial direction of rear bearing bearing shell 21, the side direction oil supply gallery in the middle of the present embodiment is along the axial direction of rear bearing bearing shell 21 and is horizontally disposed with.Rear bearing the first side direction oil supply gallery 214 and rear bearing the second side direction oil supply gallery 215 all with rear bearing radially oil supply gallery 211 be arranged in parallel, thereby lubricant oil is delivered to respectively to the axial carrying face of rear bearing 20 and supporting plane radially.
In the endface position coordinating with thrust disc thrust face 35 of rear bearing bearing shell 21, along circumferential direction, be provided with second and cross oil groove, the second mistake oil groove is communicated with the axial oil supply 213 of the rear bearing that holds oil groove 31 and rear bearing bearing shell 21 on thrust disc thrust face 35, and the lubricant oil in axial rear bearing oil supply 213 is delivered to and is held in oil groove 31 by the second mistake oil groove.
For motor rear bearing owing to only having radially load-carrying surface and an axial load-carrying surface, therefore, by the oil supply gallery of bearing machining both direction, respectively lubricant oil is caused to two end faces of this bearing, and oil supply gallery is come together in rear bearing fuel feeding distributing chute 221 in parallel.For end thrust face, in order to make distribution of lubrication oil more even, 4 oil supply galleries of mean allocation on circumference, its physical dimension feature is as follows: radial bearing surface oil supply hole d4: φ 4.5～φ 7.5mm, thrust face oil supply hole d5: φ 1～φ 4mm.
Because the side direction oil supply gallery of fore bearing 10 and rear bearing 20 and oil supply gallery are radially arranged in parallel; at lubricant oil, be delivered in the process of the thrust face of rotor and the axial load-carrying surface of bearing; do not pass through the heating of the axial mating part between rotor 30 and bearing; therefore; the oil temperature that enters thrust face can meet cooling and lubricated effect, and lubricant oil can have better viscosity, forms and stablizes dynamic pressure oil film; thereby bush material is formed to effective protection, prevent the bearing bush abrasion of bearing.
Incorporated by reference to referring to shown in Fig. 9 to Figure 14, hold oil groove 31 for being arranged on the concave inward structure on the thrust face of rotor 30, this concave inward structure forms holding space, and is communicated with the oil supply gallery on bearing unit.When work, hold oil groove 31 and coordinate formation receiving cavity with the load-carrying surface of bearing unit, thereby make lubricant oil enter and hold in oil groove 31 and accumulate by oil supply gallery.
Please specifically referring to shown in Fig. 9 to Figure 12, these figures mainly illustrate is the view structure of the axial direction of the rotor thrust face 34 that coordinates with fore bearing 10.As can be seen from the figure, hold oil groove 31 view in axial direction and be shaped as U-shaped, view along the radial direction of rotor 30 is shaped as interior concave circular arc, and this holds oil groove 31 and successively decreases along the degree of depth of the radially extension direction of rotor 30, comprise that be positioned at rotor radial direction innermost layer straight holds oil section and hold with this arc that oil section is connected and hold oil section.Holding oil groove 31 view shape in axial direction can be also ellipse or other shape.
The outward edge that holds oil groove 31 is provided with the oil unloading trough 32 that extends to the outer periphery of rotor thrust face 34 from holding oil groove 31, and this oil unloading trough 32 holds oil section with the arc that holds oil groove 31 and is connected, and by holding oil groove 31, is connected with outside emptying space.Lubricant oil lubricates and takes away after heat motor fore bearing 10, under the effect of centrifugal force, come together in and hold in oil groove 31, when holding in oil groove 31, accumulate after enough lubricant oil, oil unloading trough 32 can regulate the lubricant oil holding in oil groove 31, making to hold oil groove 31 can realize and dynamically hold oil, and maintain required pressure and the oil mass of oil film formation hydrodynamic lubrication, thereby keep the required oil mass of bearing stable operation.The sectional shape of oil unloading trough 32 is V-type or U-shaped.The oil groove 31 that holds on rotor thrust face 34 has multiplely, and is evenly distributed on rotor thrust face 34 along the circumferential direction of rotor 30, and in the middle of the present embodiment, the oil groove 31 that holds on rotor thrust face 34 has six.
It is as follows that rotor thrust face holds oil groove 31 physical dimension features: flute length L2:15～25mm, groove width w2:15～25mm, groove depth L4:3～4mm, radius of arc A:R15～R20mm, circular arc B:R15～R20mm, draining groove depth L3:1～2.5mm, draining groove width w3:1～2.5mm.
Incorporated by reference to referring to shown in Figure 13 and Figure 14, what mainly illustrate is the view structure of the axial direction of the thrust disc thrust face 35 that coordinates with rear bearing 20.As can be seen from the figure, holding oil groove 31 sectional shape is in axial direction U-shaped, along the sectional shape of the radial direction of rotor 30, is interior concave circular arc.Holding oil groove 31 sectional shape in axial direction can be also ellipse or other shape.
The outward edge that holds oil groove 31 is provided with the oil unloading trough 32 that extends to the outer periphery of thrust disc thrust face 35 from holding oil groove 31, and this oil unloading trough 32 is connected with outside emptying space holding oil groove 31.Lubricant oil lubricates and takes away after heat motor rear bearing 20, under the effect of centrifugal force, come together in and hold in oil groove 31, when holding in oil groove 31, accumulate after enough lubricant oil, oil unloading trough 32 can regulate the lubricant oil holding in oil groove 31, making to hold oil groove 31 can realize and dynamically hold oil, and maintain required pressure and the oil mass of oil film formation hydrodynamic lubrication, thereby keep the required oil mass of bearing stable operation.The sectional shape of oil unloading trough 32 is V-type or U-shaped.The oil groove 31 that holds on thrust disc thrust face 35 has multiplely, and is evenly distributed on thrust disc thrust face 35 along the circumferential direction of rotor 30, and in the middle of the present embodiment, the oil groove 31 that holds on thrust disc thrust face 35 has six.
It is as follows that thrust disc holds oil groove 31 physical dimension features: flute length L5:15～25mm, groove width w4:13～20mm, groove depth L7:1～3mm, circular arc C: R15～R20mm, draining groove depth L6:0.8～2mm, draining groove width w5:1.5～3mm.
Centrifugal compressor is in running, when lubricant oil enters bearing shell from the main fuel feeding runner of fore bearing 10 and rear bearing 20, be introduced into fuel feeding distributing chute in parallel around bearing shell one circle, then along each fuel feeding uniform flow passage in parallel, be distributed to radially load-carrying surface and axial load-carrying surface of bearing shell, through bearing shell being lubricated and taking away after heat, under centrifugal action, come together in and hold in oil groove 31, under the adjusting of drain pan 32, hold in oil groove 31 and maintain required pressure and the oil mass of oil film formation hydrodynamic lubrication, keep the required oil mass of bearing stable operation.When centrifugal compressor is during because of power down cut, the lubricant oil being accumulated in oil groove 31 slowly unloads and puts, and to bearing, provides emergency lubrication, makes bearing shell be unlikely to because of excess Temperature, to occur tile kilning phenomenon, has improved the reliability of compressor operating.
According to embodiments of the invention, chiller plant comprises above-mentioned centrifugal compressor.
From above description, can find out, the above embodiments of the present invention have realized following technique effect: motor fore bearing comprises fore bearing bearing shell and is set in the fore bearing bearing shell locating piece outside fore bearing bearing shell, fore bearing bearing shell locating piece is radially provided with the main oil supply gallery of fore bearing, on fore bearing bearing shell, comprise radially oil supply gallery and be arranged on the radially circumferential oil supply of fore bearing of the exit position of oil supply gallery of fore bearing of the fore bearing that is connected with the main oil supply gallery of fore bearing and radially run through fore bearing bearing shell, fore bearing radially comprises along the fore bearing side direction oil supply gallery that extends laterally and extend to end, fore bearing bearing shell two ends on oil supply gallery.Because there is load-carrying surface at the two ends of motor fore bearing, therefore, need on fore bearing, process radially and the two ends oil supply gallery of totally three directions.The oil supply gallery of three directions is arranged in parallel, radially oil supply gallery is for meeting the lubricated needs of the radial load between rotor and fore bearing for fore bearing, and two fore bearing side direction oil supply galleries are respectively used to meet the lubricated needs between fore bearing two ends and rotor thrust face.In fore bearing working procedure, due to lubricant oil can be respectively by fore bearing side direction oil supply gallery and fore bearing radially oil supply gallery be lubricated and lower the temperature, therefore, the lubricant oil that flows to the axial load-carrying surface of fore bearing can not cause that to enter the oil temperature of thrust face too high owing to first entering thrust structure after axial component again, exceed the temperature of bush material permission and lost efficacy, can not affect lubricant oil and form dynamic pressure oil film, thereby improve motor rear bearing reliability of operation yet.Fore bearing the first side direction oil supply gallery and fore bearing the second side direction oil supply gallery are obliquely extended to respectively the end of fore bearing bearing shell, and the sectional area of fore bearing the second side direction oil supply gallery is greater than the sectional area of fore bearing the first side direction oil supply gallery.The axial force that the bearing shaft being communicated with due to fore bearing the second side direction oil supply gallery is born to load-carrying surface is larger, therefore, make the sectional area of fore bearing the second side direction oil supply gallery be greater than the sectional area of fore bearing the first side direction oil supply gallery, when lubricant oil divides timing, can suitably distribute according to the sectional area of oil supply gallery, thereby guarantee that lubricant oil has better lubricated and cooling-down effect.
The foregoing is only the preferred embodiments of the present invention, be not limited to the present invention, for a person skilled in the art, the present invention can have various modifications and variations.Within the spirit and principles in the present invention all, any modification of doing, be equal to replacement, improvement etc., within all should being included in protection scope of the present invention.
Claims (12)
1. a motor fore bearing, comprise fore bearing bearing shell (11) and be set in the outer fore bearing bearing shell locating piece (12) of described fore bearing bearing shell (11), described fore bearing bearing shell locating piece (12) is radially provided with the main oil supply gallery of fore bearing (121), it is characterized in that, on described fore bearing bearing shell (11), comprise radially oil supply gallery (112) and be arranged on the radially circumferential oil supply of fore bearing (115) of the exit position of oil supply gallery (112) of described fore bearing of the fore bearing that is connected with the main oil supply gallery of described fore bearing (121) and radially run through described fore bearing bearing shell (11), described fore bearing radially comprises along the fore bearing side direction oil supply gallery that extends laterally and extend to described fore bearing bearing shell (11) end, two ends on oil supply gallery (112).
2. motor fore bearing according to claim 1, it is characterized in that, described fore bearing radially oil supply gallery (112) is positioned at the middle part of described fore bearing bearing shell (11), described fore bearing side direction oil supply gallery comprises fore bearing the first side direction oil supply gallery (113) and fore bearing the second side direction oil supply gallery (114), described fore bearing the first side direction oil supply gallery (113) extends to the first end end of described fore bearing bearing shell (11), described fore bearing the second side direction oil supply gallery (114) extends to the second end end of described fore bearing bearing shell (11).
3. motor fore bearing according to claim 2, it is characterized in that, described fore bearing the first side direction oil supply gallery (113) and described fore bearing the second side direction oil supply gallery (114) are along the axial direction horizontal-extending of described fore bearing bearing shell (11), and the sectional area of described fore bearing the second side direction oil supply gallery (114) is greater than the sectional area of described fore bearing the first side direction oil supply gallery (113).
4. motor fore bearing according to claim 2, it is characterized in that, described fore bearing the first side direction oil supply gallery (113) and described fore bearing the second side direction oil supply gallery (114) are obliquely extended to respectively the end of described fore bearing bearing shell (11), and the sectional area of described fore bearing the second side direction oil supply gallery (114) is greater than the sectional area of described fore bearing the first side direction oil supply gallery (113).
5. motor fore bearing according to claim 4, it is characterized in that, on the inwall of described fore bearing bearing shell (11), be provided with the axial oil supply of fore bearing (116) that is in axial direction through to the second end end of described fore bearing bearing shell (11) from the first end end of described fore bearing bearing shell (11), described fore bearing the first side direction oil supply gallery (113) is connected with the axial oil supply of described fore bearing (116) in the first end end of described fore bearing bearing shell (11), described fore bearing the second side direction oil supply gallery (114) is connected with the axial oil supply of described fore bearing (116) in the second end end of described fore bearing bearing shell (11).
6. motor fore bearing according to claim 5, it is characterized in that, the described fore bearing radially entry position of oil supply gallery (112) is provided with the fore bearing that is connected with the main oil supply gallery of described fore bearing (121) fuel feeding distributing chute in parallel (111), described fore bearing the first side direction oil supply gallery (113) and described fore bearing the second side direction oil supply gallery (114) described fore bearing parallel connection fuel feeding distributing chute (111) locate with described fore bearing radially oil supply gallery (112) be arranged in parallel.
7. motor fore bearing according to claim 6, it is characterized in that, described fore bearing the first side direction oil supply gallery (113), described fore bearing the second side direction oil supply gallery (114) and described fore bearing radially the flow area sum of oil supply gallery (112) are less than or equal to the flow area of fuel feeding distributing chute in parallel with described fore bearing (111).
8. according to the motor fore bearing described in claim 6 or 7, it is characterized in that, described fore bearing bearing shell (11) comprises radially oil supply gallery (112) of multiple described fore bearings, and multiple described fore bearings radially oil supply gallery (112) evenly arrange along the circumferential direction of described fore bearing bearing shell (11).
9. motor fore bearing according to claim 8, is characterized in that, described fore bearing fuel feeding distributing chute in parallel (111) along circumferential direction winding on the outer wall of described fore bearing bearing shell (11).
10. according to the motor fore bearing described in any one in claim 4 to 7, it is characterized in that, described fore bearing the first side direction oil supply gallery (113) comprises with the described fore bearing dispensing section (118) that radially oil supply gallery (112) is connected and is connected and extends to the extending section (119) of the first end end of described fore bearing bearing shell (11) with described dispensing section (118), and the sectional area of described extending section (119) is greater than the sectional area of described dispensing section (118).
11. 1 kinds of centrifugal compressors, comprise motor fore bearing, it is characterized in that, described motor fore bearing is the motor fore bearing described in any one in claim 1 to 10.
12. 1 kinds of chiller plants, comprise centrifugal compressor, it is characterized in that, described centrifugal compressor is the centrifugal compressor described in claim 11.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN201210015294.6A CN103206455B (en) | 2012-01-17 | 2012-01-17 | Motor front bearing and centrifugal compressor and refrigeration equipment comprising same |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201210015294.6A CN103206455B (en) | 2012-01-17 | 2012-01-17 | Motor front bearing and centrifugal compressor and refrigeration equipment comprising same |
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| CN103206455A CN103206455A (en) | 2013-07-17 |
| CN103206455B true CN103206455B (en) | 2014-04-16 |
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| CN201210015294.6A Active CN103206455B (en) | 2012-01-17 | 2012-01-17 | Motor front bearing and centrifugal compressor and refrigeration equipment comprising same |
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Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105443429A (en) * | 2014-08-06 | 2016-03-30 | 沈阳透平机械股份有限公司 | Compact non-backing plate double oil-film damp bearing and manufacturing method thereof |
| CN108425855A (en) * | 2018-05-11 | 2018-08-21 | 约翰斯顿流体科技（无锡）有限公司 | A kind of self lubricating end suction centrifugal pump |
| CN109026397A (en) * | 2018-10-21 | 2018-12-18 | 至玥腾风科技投资集团有限公司 | Bearing lubrication system and miniature gas turbine generating set |
| CN114233609B (en) * | 2021-12-08 | 2024-10-11 | 珠海格力电器股份有限公司 | Bearing cooling structure, bearing, compressor and refrigeration equipment |
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| US6158980A (en) * | 1998-06-08 | 2000-12-12 | Denso Corporation | Compressor with motor |
| WO2004005713A1 (en) * | 2002-07-04 | 2004-01-15 | Empresa Brasileira De Compressores S/A Embraco | Piston for a hermetic compressor |
| CN1518640A (en) * | 2002-04-03 | 2004-08-04 | ͬ�Ϳ�ҵ��ʽ���� | Compressor |
| CN2719455Y (en) * | 2004-09-03 | 2005-08-24 | 湖南同心科技有限公司 | High-speed electric main spindle of hydrostatic-hydrodynamic bearing |
| JP2006177239A (en) * | 2004-12-22 | 2006-07-06 | Fujitsu General Ltd | Hermetic compressor |
| CN202402487U (en) * | 2012-01-17 | 2012-08-29 | 珠海格力电器股份有限公司 | Motor front bearing and centrifugal compressor and refrigeration equipment comprising same |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6158980A (en) * | 1998-06-08 | 2000-12-12 | Denso Corporation | Compressor with motor |
| CN1518640A (en) * | 2002-04-03 | 2004-08-04 | ͬ�Ϳ�ҵ��ʽ���� | Compressor |
| WO2004005713A1 (en) * | 2002-07-04 | 2004-01-15 | Empresa Brasileira De Compressores S/A Embraco | Piston for a hermetic compressor |
| CN2719455Y (en) * | 2004-09-03 | 2005-08-24 | 湖南同心科技有限公司 | High-speed electric main spindle of hydrostatic-hydrodynamic bearing |
| JP2006177239A (en) * | 2004-12-22 | 2006-07-06 | Fujitsu General Ltd | Hermetic compressor |
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| CN103206455A (en) | 2013-07-17 |
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Inventor after: Liu Hua Inventor after: Zhong Ruixing Inventor after: Zhang Zhiping Inventor after: Xie Rong Inventor after: Jiang Nan Inventor after: Jiang Caiyun Inventor after: Fu Peng Inventor after: Yan Xiubing Inventor before: Zhong Ruixing Inventor before: Zhang Zhiping Inventor before: Xie Rong Inventor before: Jiang Nan Inventor before: Jiang Caiyun Inventor before: Fu Peng Inventor before: Yan Xiubing |