CN101624986B - Slip sheet control device of rotary compressor - Google Patents
Slip sheet control device of rotary compressor Download PDFInfo
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- CN101624986B CN101624986B CN 200910041487 CN200910041487A CN101624986B CN 101624986 B CN101624986 B CN 101624986B CN 200910041487 CN200910041487 CN 200910041487 CN 200910041487 A CN200910041487 A CN 200910041487A CN 101624986 B CN101624986 B CN 101624986B
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Abstract
The invention discloses a slip sheet control device of a rotary compressor, comprising a compression assembly and a motor assembly which are arranged in a sealing housing, wherein the compression assembly comprises a first cylinder, a second cylinder, an eccentric crank shaft, an upper bearing, a lower bearing and a middle clapboard arranged between the first cylinder and the second cylinder; the upper bearing and the lower bearing support the eccentric crank shaft; a first piston, a second piston, a first slip sheet slot and a second slip sheet slot are respectively arranged in each cylinder; a fist slip sheet and a compression spring are arranged in the first slip slot, a second slip sheet is arranged in the second slip sheet slot, and the second slip sheet slot is communicated with a slip sheet cavity which is communicated with a pressure transmission tube; a magnet absorbing and braking the second slip sheet is arranged on the bearing and the middle clapboard in the slip sheet cavity at the back of the second slip sheet; the back of the second slip sheet is provided with a small end which moves in the same direction with the second slip sheet and improves the movement reliability thereof, and one side of the small end, which faces to the magnet, is provided with a clearance space. The invention has the characteristics of reliable performance, high safety degree and long service life.
Description
Technical field
The present invention relates to the device for controlling sliding vane of a kind of rotary compressor, particularly a kind of rotary compressor.
Background technique
Common twin-tub or multi-cylinder rotary compressor, as shown in Figure 1, the compressor of sealing is provided with compression assembly 1 and electric machine assembly 2.Compression assembly comprises two cylinders, be respectively first cylinder 3.1 and second cylinder 3.2, be respectively arranged with the first piston 4.1 and second piston 4.2 in each cylinder, and be separately positioned on first slide plate 6.1 and second slide plate 6.2 in cylinder first vane slot 5.1 and second vane slot 5.2, the eccentric crankshaft of driven plunger, eccentric crankshaft comprises eccentric crankshaft main shaft 7.1 and eccentric crankshaft countershaft 7.2, support the upper bearing (metal) 8.1 and the lower bearing 8.2 of eccentric crankshaft, separate the central diaphragm 9 of two cylinders up and down, the eccentric crankshaft that drives by electric machine assembly 2 passes torque to the first piston 4.1 and second piston 4.2, the pressurized gas of cylinder compression are discharged to system side by enclosure interior from discharge pipe 10, therefore, pressing in the housing is the high pressure side.The back of first slide plate 6.1 of first cylinder 3.1 is connected with the pressure spring 6.1.1 that promotes the slide plate action, the motion of slide plate is provided by the elastic force of 6.1.1 during compressor start, is just moved by high pressure in first vane slot 5.1 and common first slide plate 6.1 that promotes of pressure spring 6.1.1 behind the compressor start; Second slide plate, 6.2 backs of second cylinder 3.2 then do not promote the spring of vane motion, and second vane slot 5.2 and withdrawing hole 5.4 forms airtight slide plate chambeies and be connected an end of penstock 11; Penstock 11 can optionally flow to airtight slide plate chamber with exhaust high pressure in the compressor housing and the switching of air-breathing low pressure, and some scheme of optionally switching air pressure has certainly been used a switching valve 12.
When being high pressure in the penstock 11, then second slide plate, 6.2 proper motion work, cylinder has compression exhaust; When being low pressure in the penstock 11, then second slide plate 6.2 stops in the vane slot 5.2, and cylinder does not compress no exhaust; Second cylinder 3.2 switches between exhaust and not exhaust, and then compressor forms the variation of air displacement, and the transfiguration function is achieved.Here mention and in penstock 11, be low pressure, be that the slide plate chamber is when being low pressure, then second slide plate 6.2 stops in the vane slot 5.2, yet in fact because fluctuation can appear in the low pressure in low pressure in the cylinder 3.2 and slide plate chamber, and second slide plate 6.2 itself also can produce vibration owing to the running of compressor, these two factors just are easy to make second slide plate 6.2 to be projected in second cylinder 3.2 and produce collision with second piston 4.2, rebound after the collision, collide with slide plate chamber wall again, so form abominable noise, see accompanying drawing 9, even the broken invalid of slide plate and piston might occur.
For overcoming the above problems, the inventor once proposed to be provided with the magnet of absorption slide plate around slide plate, utilize magnetic force to improve scheme air-breathing and exhaust pressure control vane motion, and this scheme had been improved the control effect of slide plate greatly.Through further research invention, on indivedual compressors, use the problem that institute's generations structural design is limited to, the scheme below having proposed by improving former scheme.
Summary of the invention
Purpose of the present invention aims to provide a kind of simple and reasonable, reliable performance, safety rate height, long service life, reduces because the device for controlling sliding vane of the rotary compressor of the noise that vibration causes and the destruction that may occur greatly, to overcome deficiency of the prior art.
Press the device for controlling sliding vane of a kind of rotary compressor of this purpose design, comprise the compression assembly and the electric machine assembly that are arranged in the closed shell, compression assembly comprises first cylinder, second cylinder, eccentric crankshaft, support the metal (upper of eccentric crankshaft and be arranged on first cylinder and second cylinder between central diaphragm, be respectively arranged with the first piston and second piston in each cylinder, first vane slot and second vane slot, be provided with first slide plate and pressure spring in first vane slot, be provided with second slide plate in second vane slot, second vane slot communicates with the slide plate chamber, the slide plate chamber communicates with penstock, the bearing at the place, slide plate chamber at the second slide plate back and central diaphragm are provided with the magnet of absorption braking second slide plate, its structure characteristic is that the back of second slide plate is provided with the small end that moves in the same way with second slide plate and improve its motion credibility, and small end is provided with clearance position towards a side of magnet.
The described small end end face of an end outwardly is littler than the end face of second slide plate, small end outwardly the distance between the end face edge of second slide plate of the end face edge of an end and its homonymy more than or equal to 1mm.
Described small end is square or trapezoidal in the side view of the second cylinder circumferencial direction.
The present invention is provided with the magnet of absorption slide plate around second slide plate, when utilizing magnetic force to improve second slide plate control effect, set up the small end that moves in the same way with second slide plate and improve its motion credibility at the second slide plate back, the problem that institute's structural design that produces is limited to when having solved former scheme and using on indivedual compressors, and further improved the reliability of second slide plate, reduce its abrasion loss, reduce noise that causes owing to vibration and the destruction that may occur greatly, thereby prolonged the working life of second slide plate.
Description of drawings
Fig. 1 is the sectional structure schematic representation of prior art.
Fig. 2 is the structural representation of the embodiment in the early stage related invention patent of the inventor.
Fig. 3 is that B-B among Fig. 2 is to the schematic representation of broken section structure and slide plate halted state.
Fig. 4 is in the early stage inventive embodiments, and second slide plate moves to and contacts with the external diameter of second piston and the structural representation of second vane motion near the position of magnet the time.
Fig. 5 is the A place structure for amplifying schematic representation among Fig. 4.
Fig. 6 is the structural representation of first embodiment's slide plate halted state among the present invention.
Fig. 7 contact with the external diameter of second piston for first embodiment, second slide plate among the present invention moves to and the structural representation of second vane motion during to the position of close magnet.
Fig. 8 is the C place structure for amplifying schematic representation among Fig. 7.
Fig. 9 contact with the external diameter of second piston for second embodiment, second slide plate among the present invention moves to and the structural representation of second vane motion during to the position of close magnet.
Figure 10 is the vibration test figure as a result of slide plate of the prior art.
Figure 11 is the vibration test of the slide plate among the present invention figure as a result.
Among the figure: 1 is compression assembly, and 2 is electric machine assembly, and 3.1 is first cylinder, 3.2 be second cylinder, 4.1 is first piston, 4.2 is second piston, 5.1 be first vane slot, 5.2 is second vane slot, 5.3 is the slide plate chamber, 5.4 be the withdrawing hole, 6.1 is first slide plate, 6.1.1 is a pressure spring, 6.2 be second slide plate, 7.1 be main shaft, 7.2 is countershaft, 8.1 is upper bearing (metal), 8.2 be lower bearing, 9 is central diaphragm, and 10 is discharge pipe, and 11 is penstock, 12 is switching valve, 13.1 be first magnet, 13.2 is second magnet, 14 inlet holes when being cylinder operation.
Embodiment
Below in conjunction with drawings and Examples the present invention is further described.
Below adopt with background technique in identical reference character describe.
Reach understanding for convenience of explanation, at first the technological scheme before the present invention is carried out following quoting: referring to Fig. 2-Fig. 4 and Fig. 8, first magnet 13.1 in the device for controlling sliding vane of rotary compressor and second magnet 13.2 are separately positioned on the central diaphragm 9 and lower bearing 8.2 at the place, slide plate chamber that is positioned at second slide plate, 6.2 backs, second slide plate 6.2 can be by first magnet 13.1 and 13.2 absorption of second magnet, and all the time away from and be not projected in second cylinder 3.2, so just can not bump with second piston 4.2 yet.Wherein, the slide plate chamber can be made of withdrawing hole 5.4 or other forms of hole etc.
When second slide plate 6.2 quits work, when being in the position of just withdrawing from second cylinder, 3.2 inwalls, the back of second slide plate 6.2 can not stride across the center line of first magnet 13.1 and second magnet 13.2; Promptly the first spacing d1 between the external diameter of an end of second slide plate 6.2 and second piston 4.2 is greater than zero the time, the second spacing d2 between the center line of the other end of second slide plate 6.2 and first magnet 13.1 and second magnet 13.2 is more than or equal to zero, so just can better bring into play the magnetic force of first magnet 13.1 and second magnet 13.2, prevent of the direction motion of second slide plate 6.2 to second piston 4.2.
In addition, when second slide plate 6.2 contacts proper functioning with second piston, the rear end and the magnet of second slide plate 6.2 maintain a certain distance, promptly the first spacing d1 between the external diameter of an end of second slide plate 6.2 and second piston 4.2 equals zero and second slide plate 6.2 when moving to position near magnet, the 3rd spacing d3 between the end of the other end of second slide plate 6.2 and first magnet 13.1 and second magnet 13.2 is greater than 0.2mm, and smaller or equal to 5mm; This technological scheme can further solve the another one problem, will describe in detail below.
When compressor start, first cylinder, 3.1 beginning compression refrigerants, yet this moment, the exhaust pressure of air-conditioning system progressively raise, pressure for fear of the second slide plate chamber progressively raises, second slide plate 6.2 is subjected to unsettled thrust, then must control in the pressure-activated process in the second slide plate chamber and be always low pressure, the pressure controlled valve 12 that joins with penstock 11 can not omit so, yet, if after adopting technological scheme provided by the invention, then can omit pressure controlled valve 12, thereby reach the purpose that reduces fabricating cost, its reason is when adopting " the first spacing d1 between an end of second slide plate 6.2 and the external diameter of second piston 4.2 is greater than zero time; the second spacing d2 between the center line of the other end of second slide plate 6.2 and first magnet 13.1 and second magnet 13.2 is more than or equal to zero " scheme, when the magnetic force of first magnet 13.1 and second magnet 13.2 is designed into when enough big, no matter which kind of unsettled pressure the second slide plate chamber is in the compressor start process, second slide plate 6.2 all can be adsorbed by first magnet 13.1 and second magnet 13.2, and motion that can be stable.
And after compressor start is finished, when exhaust pressure is enough big steady pressure, its pressure is enough to overcome the magnetic force of first magnet 13.1 and second magnet 13.2 and drives the motion of second slide plate 6.2, promptly in movement process, adopt " when the first spacing d1 between the external diameter of an end of second slide plate 6.2 and second piston 4.2 equals zero and second slide plate 6.2 when moving to the position of close magnet; the 3rd spacing d3 between the end of the other end of second slide plate 6.2 and first magnet 13.1 and second magnet 13.2 is greater than 0.2mm; and smaller or equal to 5mm " scheme the time, second slide plate 6.2 is subjected to magnetic force little, and magnetic force can not influence the proper motion of second slide plate.
Because in the start-up course, the pressure in the second slide plate chamber can be left it with system change, do not need to do control by force, so can omit pressure controlled valve 12, reduce fabricating cost significantly.The magnetic pole of first magnet 13.1 and second magnet 13.2 is arranged on the side towards slide plate, effect that can more effective performance magnetic force.
After such scheme used the back, the vibration of second slide plate 6.2 reduced greatly, and the quality and the reliability of compressor improve greatly.
But because the architectural difference of compressor, indivedual compressor arrangements produce following design limitations when adopting such scheme: as previously mentioned, when second slide plate 6.2 contacts proper functioning with second piston, the rear end and the magnet of second slide plate 6.2 maintain a certain distance, promptly the first spacing d1 between the external diameter of an end of second slide plate 6.2 and second piston 4.2 equals zero and second slide plate 6.2 when moving to position near magnet, the 3rd spacing d3 between the end of the other end of second slide plate 6.2 and first magnet 13.1 and second magnet 13.2 is greater than 0.2mm, and smaller or equal to 5mm.
Be understood that, when satisfying work, the rear end and the magnet of second slide plate 6.2 maintain a certain distance, then the rear end size of second slide plate 6.2 will be shorter, the length of its rear end can not be elongated to during work has overlapping with magnet, the total length of second slide plate 6.2 like this will be shorter, effective contact length of short more then second slide plate 6.2 of second slide plate 6.2 and second slide plate, 6.2 cell walls is just short more, and this change will cause the motion credibility of second slide plate 6.2 to reduce and the abrasion of second slide plate 6.2 and cell wall increase, it is very outstanding that this problem will become on some compressor arrangement, also become a design difficulty, the solution of the present invention then can address this problem.
First embodiment
Referring to Fig. 5, Fig. 6 and Fig. 9, be provided with the small end that moves in the same way with second slide plate 6.2 and improve its motion credibility at the back of second slide plate 6.2, small end is provided with clearance position towards a side of magnet.The purpose that this clearance position is set is exactly in order to satisfy the requirement in the such scheme.The simple practice is to leave two straight cut between the back of second slide plate 6.2, with the back Cross section Design of second slide plate 6.2 is convex shape, be that small end is square in the side view of second cylinder, 3.2 circumferencial directions, perhaps, also can do following understanding: the cross section along second slide plate, 6.2 moving direction of small end is square.
Among Fig. 5, when second slide plate 6.2 quits work, when being in the position of just withdrawing from second cylinder, 3.2 inwalls, the back of second slide plate 6.2 can not stride across the center line of first magnet 13.1 and second magnet 13.2, promptly same satisfy when the first spacing d1 greater than zero the time, the second spacing d2 is more than or equal to zero;
Among Fig. 6, when second slide plate 6.2 contacts proper functioning with second piston, the rear end and the magnet of second slide plate 6.2 maintain a certain distance, promptly when the first spacing d1 equals zero, the 3rd spacing d3 is greater than 0.2mm, and smaller or equal to 5mm, so satisfy the requirement of former scheme equally, but total length L ' the add length of small end of second slide plate 6.2 of this moment for the raw footage L of former second slide plate 6.2, this total length L ' longer than the raw footage L of former second slide plate 6.2 significantly is so can satisfy the requirement of slide plate reliability and wear resistance requirement to length fully.
The small end end face of an end outwardly is littler than the end face of second slide plate 6.2, small end outwardly between the end face edge of second slide plate of the end face edge of an end and its homonymy apart from d5 more than or equal to 1mm, be straight cut two edges apart from d5 more than or equal to 1mm, just can effectively eliminate the magnetic force that second slide plate, 6.2 working staties are subjected to.
After adopting such scheme provided by the invention, the vibration of second slide plate 6.2 reduces greatly, sees Fig. 9, and the quality and the reliability of compressor improve greatly.
Second embodiment
Referring to Fig. 7 and Fig. 9, offer two angular cuts at the back of second slide plate 6.2, promptly when being trapezoidal, its implementation result is with first embodiment in the side view of second cylinder, 3.2 circumferencial directions for small end, but the processibility of its slide plate improves, i.e. low the and work efficiency height of processing cost.
Certainly, also can offer the curve bath of indent, also can reach with the identical effect of first embodiment in the upper and lower side at the back of second slide plate 6.2.
All the other are not stated part and see first embodiment, no longer repeat.
Claims (3)
1. the device for controlling sliding vane of a rotary compressor, comprise the compression assembly (1) and the electric machine assembly (2) that are arranged in the closed shell, compression assembly comprises first cylinder (3.1), second cylinder (3.2), eccentric crankshaft, support the metal (upper of eccentric crankshaft and be arranged on first cylinder and second cylinder between central diaphragm (9), be respectively arranged with first piston (4.1) and second piston (4.2) in each cylinder, first vane slot (5.1) and second vane slot (5.2), be provided with first slide plate (6.1) and pressure spring (6.1.1) in first vane slot, be provided with second slide plate (6.2) in second vane slot, second vane slot communicates with the slide plate chamber, the slide plate chamber communicates with penstock (11), the bearing at the place, slide plate chamber at the second slide plate back and central diaphragm are provided with the magnet of absorption braking second slide plate, the back that it is characterized in that second slide plate is provided with the small end that moves in the same way with second slide plate and improve its motion credibility, and small end is provided with clearance position towards a side of magnet.
2. the device for controlling sliding vane of rotary compressor according to claim 1, the end face of an end is littler than the end face of second slide plate (6.2) outwardly to it is characterized in that described small end, small end outwardly the distance (d5) between the end face edge of second slide plate of the end face edge of an end and its homonymy more than or equal to 1mm.
3. the device for controlling sliding vane of rotary compressor according to claim 1 is characterized in that described small end is square or trapezoidal in the side view of second cylinder (3.2) circumferencial direction.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200910041487 CN101624986B (en) | 2009-07-24 | 2009-07-24 | Slip sheet control device of rotary compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200910041487 CN101624986B (en) | 2009-07-24 | 2009-07-24 | Slip sheet control device of rotary compressor |
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| Publication Number | Publication Date |
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| CN101624986A CN101624986A (en) | 2010-01-13 |
| CN101624986B true CN101624986B (en) | 2011-07-20 |
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| CN 200910041487 Active CN101624986B (en) | 2009-07-24 | 2009-07-24 | Slip sheet control device of rotary compressor |
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Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103511264B (en) * | 2013-08-01 | 2016-03-16 | 广东美芝制冷设备有限公司 | Rotary compressor |
| CN104454529B (en) * | 2014-12-04 | 2017-02-22 | 广东美芝制冷设备有限公司 | Compression mechanism for rotary compressor and rotary compressor with same |
| CN104454530B (en) * | 2014-12-04 | 2016-06-29 | 广东美芝制冷设备有限公司 | Compressing mechanism and there is its rotary compressor for rotary compressor |
| CN105114306B (en) * | 2015-09-01 | 2018-02-13 | 广东美芝制冷设备有限公司 | Rotary compression thermomechanical components and there is its freezing cycle device |
| CN105805003B (en) * | 2016-03-04 | 2018-03-06 | 广东美芝制冷设备有限公司 | Multi-cylinder rotary compressor and rotary compressor |
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