CN101504231B - Two-stage rotary vane type expansion machine - Google Patents
Two-stage rotary vane type expansion machine Download PDFInfo
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- CN101504231B CN101504231B CN2009100214090A CN200910021409A CN101504231B CN 101504231 B CN101504231 B CN 101504231B CN 2009100214090 A CN2009100214090 A CN 2009100214090A CN 200910021409 A CN200910021409 A CN 200910021409A CN 101504231 B CN101504231 B CN 101504231B
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Abstract
The invention belongs to the field of refrigeration technology and equipment and in particular relates to a two-stage rotary vane expansion machine for recovering energy in a refrigeration (heat pump) system. The two-stage rotary vane expansion machine comprises a cylinder body, a rotor, a sliding blade, a bearing, a bearing seat and an end cap; the expansion machine has two asymmetric working chambers; the internal contour lines of the cylinder body of the expansion machine are asymmetric smooth curves; the rotor is provided with a sliding blade groove; a spring is arranged between the bottom of the sliding blade and the rotor; an air inlet is arranged on the bearing seat; the cylinder body is provided with the working chambers and intake and exhaust air ducts; and the end cap is provided with a general air vent. The two-stage rotary vane expansion machine of the invention has a volume ratio of about 7.5, is used to replace a throttle valve in the conventional vapor compression refrigeration (heat pump) system, and can expand R410A under a standard air conditioner working condition from a condenser outlet working condition to an evaporator inlet working condition while recovering expansion work generated in an expansion process at the same time, reducing system energy consumption and improving system energy efficiency ratio.
Description
Technical field
The invention belongs to Refrigeration Technique and art of refrigeration units, be specifically related to a kind of two-stage rotary vane type expansion machine that refrigeration (heat pump) system capacity reclaims that is used for.
Background technology
Along with improving constantly of human living standard, the application of refrigeration (heat pump) system in productive life is increasing, and the ratio of its power consumption in total energy consumption also constantly raises.Therefore reduce energy consumption, the raising system effectiveness of refrigeration (heat pump) system, it is particularly important to seem under the background of global energy growing tension.
In tradition refrigeration (heat pump) system, working medium is by the throttling action of choke valve, flow to gas, the liquid two-phase of low-temp low-pressure from the liquid phase section of HTHP, then enters evaporimeter and obtains cold.In throttling process, the temperature of working medium, pressure reduce, and produce irreversible loss (restriction loss).Therefore, if can reduce and recycle this part restriction loss, will significantly improve the whole efficiency of refrigeration (heat pump) system, reach the purpose that reduces system energy consumption.
Decompressor is a kind of universal machine that pressure can be able to be converted into mechanical or electrical energy.In refrigeration (heat pump) system, substitute the temperature and pressure that choke valve not only can reduce working medium with decompressor, can also reclaim the pressure energy of working medium in expansion process simultaneously.Drive auxiliary compressor work as the energy that reclaims with decompressor, can carry out precommpression, thereby under the condition of not influence system refrigeration (heating) amount, can reduce the input work of system's main compressor, reduce system energy consumption, improve the Energy Efficiency Ratio of system working medium.
In present widely used steam compression type refrigerating (heat pump) system, the volumetric ratio of working medium is bigger, and this is big difficulty for manufacturing and designing of decompressor brings.Therefore, development and application refrigeration (heat pump) system capacity reclaims decompressor and still is in the starting stage at present, and practical application is also less.
Traditional rotary vane type expansion machine is a kind of single-stage expansion machine, and the volumetric ratio that can realize limited (3.0～4.0) can not directly satisfy big volumetric ratio requirement in steam compression type refrigerating (heat pump) system.
Summary of the invention
At the less deficiency of the rotary vane type expansion machine volumetric ratio of above-mentioned prior art, the objective of the invention is to, provide a kind of simple in structure, reliable operation, rotary vane type expansion machine with double expansion process of big volumetric ratio.
In order to realize above-mentioned task, the present invention takes following technical solution:
A kind of two-stage rotary vane type expansion machine, comprise cylinder body, rotor, slide plate, bearing, bearing block and end cap, it is characterized in that, rotor is divided into two asymmetric working chambers with cylinder body along Y-axis, be respectively the one-level working chamber, the secondary work chamber, the inner outline of the cylinder body axis vertical section of decompressor is a smooth curve, by one-level work molded lines, the secondary work molded lines constitutes, offer vane slot on the rotor, be provided with spring between slide plate bottom and the rotor, air inlet is opened on the bearing block, the one-level working chamber in the cylinder body, the secondary work chamber is communicated with by middle entering and exhaust channel, is arranged in the cylinder body to dividing two sections along cylinder axis; The secondary exhaust duct be arranged in parallel along the bearing block axis, and is connected with the bearing block inner chamber body, offers total exhaust duct on the end cap.
Described one-level work molded lines is connected by two sections sealing curve bgc, b ' hc ' with the secondary work molded lines, and the sealing curve is respectively circular arc, and the radius of this circular arc equates with the radius of rotor (10).
Described one-level work molded lines and secondary work molded lines constitute by working curve and easement curve, the working curve of described one-level work molded lines and the secondary work molded lines all curvature with the sealing curve is different, and working curve is connected with the sealing curve by easement curve.
Described one-level work molded lines is a simple harmonic curve, and the secondary work molded lines is oval simple harmonic curve.
Working chamber volume when the working chamber volume when described decompressor one-level working chamber begins exhaust equals compound expansion working chamber air inlet end.
The easement curve of described one-level work molded lines and secondary work molded lines is the high-order moment curve.
Description of drawings
The easement curve of described one-level work molded lines and secondary work molded lines is continuous with working curve separately and sealing curve junction three order derivatives.
Offer vane slot (11) on the described rotor (10), its incline direction is identical with the rotor direction, and the root size of vane slot is greater than the size of groove body.
Described decompressor is except air inlet and gas outlet and outside the connection, and the air inlet between the double expansion, exhaust passage all are arranged on decompressor inside, connect without exterior line.
Two-stage rotary vane type expansion machine of the present invention is compared the single-stage rotary vane type expansion machine, and it can realize the volumetric ratio about 7.5. Be used for substituting the choke valve of traditional steam compression type refrigerating (heat pump) system, can be with the R410A under the standard air conditioning condition, from condensing pressure, condensate port temperature expansion to evaporating pressure, evaporating temperature, reclaim simultaneously and export the expansion work that cold-producing medium produces in expansion process. Be implemented on the basis that does not affect cooling system (heating) ability, reduce system energy consumption, improve systematic energy efficiency ratio.
Fig. 1 is the overall structure schematic diagram of decompressor;
Fig. 2 is the cylinder outline line schematic diagram of decompressor;
Fig. 3 is the bearing block and the end cap position partial sectional view of decompressor;
Fig. 4 is the working chamber schematic diagram of decompressor, and the A-A that is Fig. 3 is to cutaway view;
Fig. 5 is the expansion machine rotor cross sectional representation;
Fig. 6 is the entering and exhaust channel figure that offers on the decompressor cylinder body, and the D-D that is Fig. 4 is to cutaway view;
Fig. 7 is the secondary exhaust outlet schematic diagram of decompressor, and the B-B that is Fig. 3 is to cutaway view;
The specific embodiment
Fig. 8 is the exhaust duct schematic diagram of decompressor, is that the C-C of Fig. 4 is to cutaway view;
Fig. 9 is the 3D solid cutaway view of expander shaft bearing;
Figure 10 is the 3D solid cutaway view of decompressor cylinder body.
Component part numbers in the accompanying drawing: end cap 1, bearing block 2, cylinder body 3, bearing block 4, end cap 5, key 6, shaft seal 7, secondary exhaust duct 8, angular contact bearing 9, rotor 10, slide plate 11, vane slot 12, flat spring 13, total exhaust duct 14, secondary work molded lines 15, secondary work chamber 16, middle entering and exhaust channel 17, one-level work molded lines 18, one-level working chamber 19, one-level air intake duct 20, helical spring 21, air inlet through hole 22, sealing strip 23.
The present invention is described in further detail below in conjunction with accompanying drawing.
As shown in Figure 1, decompressor of the present invention comprises cylinder body 3, and two end faces of cylinder body 3 connect with bearing block 2 and bearing block 4 usefulness screws respectively, is provided with sealing strip 23 between two end faces of two bearing blocks and cylinder body 3, realizes the sealing axial to the decompressor working chamber.
The outer ring of pair of bearings 9 is installed in respectively in bearing block 2, the bearing block 4, by the sleeve on end cap 1 and the end cap 5 bearing 9 is carried out axial restraint; The inner ring of bearing 9 is installed on the rotor 10, and by the shaft shoulder bearing 9 other ends is carried out axial restraint.End cap 1 and end cap 5 are bound up on bearing block 2 and the bearing block 4 with screw respectively, and rotor 10 stretches out from end cap 5 centers, the through hole installed inside axle envelope 7 of stretching out at end cap 5 rotors 10, rotor 10 by key 6 can with auxiliary compressor or generator electric, outputting power.
A secondary work molded lines as shown in Figure 2, decompressor of the present invention is the double expansion machine, and decompressor working chamber work molded lines is the combination molded lines, and the one-level work molded lines 18 of decompressor is by working curve afa ', and easement curve ab, a ' b ' constitute; The cylinder body secondary work molded lines 15 of described decompressor is by working curve ded ', easement curve cd, c ' d ' constitute, the smooth curve of the sealing that one-level work molded lines 18 and secondary work molded lines 15 coupling parts are made of sealing curve bgc, b ' hc ', the sealing curve is one section circular arc, its radius is identical with the radius of rotor 10, by the radial seal between matched in clearance realization expansion machine rotor 10 and the cylinder 3.The working curve afa ' of one-level work molded lines 18 is a simple harmonic curve, the working curve ded ' of secondary work molded lines 15 is oval simple harmonic curve, and the working chamber volume that the geometric parameter of two-stage different operating line must satisfy working chamber volume when making one-level working chamber 19 beginning exhausts when finishing with 16 air inlets of secondary work chamber equates (see figure 4).Because working curve is different with the curvature of sealing curve, the two directly links to each other wedge angle or flex point can occur, and the force-bearing situation of severe exacerbation slide plate reduces noise increase, functional reliability and the life-span of decompressor.Therefore need be connected with easement curve between working curve and the sealing curve, be respectively one-level cylinder easement curve ab and easement curve a ' b ', secondary cylinder easement curve cd and easement curve c ' d ', easement curve is the high-order moment curve, it is continuous to satisfy itself and working curve and sealing curve junction three order derivatives, make slide plate steadily excessive, stressedly evenly do not undergo mutation.
As shown in Figure 3, total exhaust duct 14 of decompressor of the present invention is opened on the end cap 1, and working medium flows out decompressor from total exhaust duct 14, and rotor stretches out from end cap 5 centers, installation shaft envelope 7 on the end cap 5, the sleeve that end cap 1 and end cap 5 stretch out carries out axial restraint to the outer ring of bearing 9.
As shown in Figure 4, the rotor 10 of decompressor of the present invention is divided into two asymmetric working chambers with cylinder body along Y-axis, be respectively one-level working chamber 19, secondary work chamber 16, rotor 10 is by rotation (facing from rotor 10 external part directions) counterclockwise, slide plate 11 is divided into eight chambers with cylinder, the working medium that enters decompressor at first enters the one-level working chamber 19 of decompressor from being opened in one-level air intake ducts 20 in the cylinder body 3, rotation along with rotor, when slide plate 11 turns over one-level air intake duct 20, the working chamber complete closed, the one-level air inlet finishes.Under the effect of pressure reduction, the working medium that is sealed in the one-level working chamber 19 constantly expands, promote slide plate 11 and rotor 10 rotations, when one-level working chamber 19 reaches its maximum volume, the i point of entering and exhaust channel 17 in the middle of slide plate goes to just, the beginning exhaust, one-level expands and finishes, working medium flows out one-level working chamber 19 from middle entering and exhaust channel 17, enters secondary work chamber 16.The intake process of the intake process in secondary work chamber 16 and one-level working chamber 19 is similar, middle entering and exhaust channel 17 is the position that 16 air inlets of secondary work chamber finish with the some j that cylinder intersects, promptly the secondary work chamber 16 of decompressor isolates with middle entering and exhaust channel 17 when slide plate 11 goes to the j point, and the secondary air inlet finishes.The volume of (slide plate 11 goes to an i) was identical when the volume in (slide plate 11 goes to a j) secondary work chamber 16 was with the 19 beginning exhausts of one-level working chamber when the secondary air inlet finished, and double expansion can carry out continuously like this.Along with being rotated further of slide plate, working medium constantly expands, and the volume in secondary work chamber 16 increases gradually, and begins exhaust when reaching its maximum volume.Leave the decompressor working chamber through the working medium behind the double expansion through secondary exhaust duct 8, finish whole expansion process.Offer eight vane slots 12 on the rotor 10, vane slot and cross axes intersect, its incline direction is identical with the rotor direction of rotation, slide plate 11 embeds in the vane slot 12, slide plate 11 is along with the rotation of rotor 10, and under the effect of the elastic force of the spring of installing in centrifugal force and bottom 13, slide plate 11 extends radially vane slot 12, top and cylinder body wall fit tightly, and reciprocating in vane slot 12 along the curve shape of cylinder body 3 walls.The degree of depth of vane slot 12 need satisfy at slide plate 11 tops (slide plate 11 is embedded in the vane slot 12 fully) when concordant with vane slot 12 tops, the distance of 1～2mm should be left in slide plate 11 bottoms apart from vane slot 12 bottoms, and vane slot 12 strengthens near the cross-sectional area of bottom, its objective is in order to allow vane slot 12 bottoms form the exhaust passage that is communicated with the bearing bore at rotor 10 two ends, so that the layout of secondary exhaust gear and lubricated bearing 9.Slide plate is packed into together with the spring that certain pretension is arranged behind the vane slot, and initial tension of spring can guarantee that the arbitrarily angled and cylinder wall surface of slide plate when decompressor is worked fit.Because one-level, two working chambers of secondary are asymmetric, the maximum lift of slide plate in two working chambers is also inequality, and the physical dimension of used slide plate will satisfy the requirement in two different operating chambeies simultaneously.
The slide plate 11 bottom mounting spring of decompressor of the present invention, spring can be selected flat spring or helical spring, two kinds of springs when mounted and between slide plate 11 and the vane slot 12 all fastener-free connect.For guaranteeing that slide plate 11 all radially is in the state of stretching out along rotor 10 at any time in vane slot 12, its top and work molded lines are fitted, form the working chamber of sealing, need the spring pretension.
One-level air intake duct 20 be arranged in parallel with Y-axis, be opened in one-level working chamber 19 1 sides, middle entering and exhaust channel 17 is crossed over one-level working chamber 19 and secondary work chamber 16, the exhaust duct that is one-level working chamber 19 is again the air intake duct in secondary work chamber 16, and secondary work chamber 16 is directly introduced in the exhaust of one-level working chamber 19.
As shown in Figure 6, the one-level air intake duct 20 of decompressor of the present invention and middle entering and exhaust channel 17, in cylinder body 3, divide two sections settings on axially, air inlet through hole 22 connects two sections one-level air intake ducts 20, air inlet through hole 22 is end sealing on cylinder body 3, and the openend that links with the decompressor external world is positioned on the bearing block 2, after cold-producing medium flows out condenser, enter decompressor from air inlet through hole 22, shunt again from two sections one-level air intake ducts 20 and enter the decompressor working chamber.
As shown in Figure 7, the secondary exhaust duct 8 of decompressor of the present invention communicates with bearing block 4, and working medium enters in the bearing block 4 after flowing out from the decompressor working chamber by secondary exhaust duct 8, and this figure only shows the position of secondary exhaust duct 8 in the bearing block 4.
As Fig. 8, shown in Figure 9, the secondary exhaust duct 8 of decompressor of the present invention be arranged in parallel along bearing block 2,4 axis, and is connected with bearing block 2,4 inner chamber body.The cold-producing medium that is in the secondary exhaust phase flows out by secondary exhaust duct 8 vertically from secondary work chamber 16, and flows into respectively in the bearing bore of bearing block 2 and bearing block 4.The cold-producing medium of inflow bearing block 4 flows into again in the bearing block 2 vertically by the through hole and the gap between the rolling bearing ball of vane slot 12 bottoms, then by total exhaust duct 14 final decompressors that flow out.Contain lubricating oil in the cold-producing medium, through rolling bearing the time, can be lubricated it.
As Figure 10 is the 3D solid cutaway view of decompressor cylinder body, and one-level air intake duct 20 and middle entering and exhaust channel 17 divide two sections to be opened in the cylinder body respectively, and air inlet through hole 22 is communicated with two sections one-level air intake ducts 20.
Claims (9)
1. two-stage rotary vane type expansion machine, comprise cylinder body (3), rotor (10), slide plate (11), bearing (9), bearing block (2,4) and end cap (1), it is characterized in that, rotor (10) is divided into two asymmetric working chambers with cylinder body (3) along Y-axis, be respectively one-level working chamber (19), secondary work chamber (16), the inner outline of the axis normal section of decompressor cylinder body (3) is a smooth curve, by one-level work molded lines (18), secondary work molded lines (15) constitutes, offer vane slot (12) on the rotor (10), be provided with spring (13) between slide plate (11) bottom and the rotor, air inlet is opened on the bearing block (2), one-level working chamber (19) in the cylinder body, secondary work chamber (16) is communicated with by middle entering and exhaust channel (17), is arranged in the cylinder body to dividing two sections along cylinder axis; Secondary exhaust duct (8) be arranged in parallel along bearing block (2,4) axis, and is connected with the bearing block inner chamber body, offers total exhaust duct (14) on the end cap (1).
2. according to the described two-stage rotary vane type expansion machine of claim 1, it is characterized in that: described one-level work molded lines is connected by two sections sealing curves (bgc, b ' hc ') with the secondary work molded lines, the sealing curve is respectively circular arc, and the radius of this circular arc equates with the radius of rotor (10).
3. two-stage rotary vane type expansion machine according to claim 2, it is characterized in that: described one-level work molded lines and secondary work molded lines constitute by working curve and easement curve, the working curve of described one-level work molded lines and the secondary work molded lines all curvature with the sealing curve is different, and working curve is connected with the sealing curve by easement curve.
4. two-stage rotary vane type expansion machine according to claim 3 is characterized in that: one-level work molded lines is a simple harmonic curve, and the secondary work molded lines is oval simple harmonic curve.
5. according to claim 1 or 4 described two-stage rotary vane type expansion machines, it is characterized in that: the working chamber volume the when working chamber volume when described decompressor one-level working chamber begins exhaust equals the air inlet end of secondary work chamber.
6. two-stage rotary vane type expansion machine according to claim 5 is characterized in that: the easement curve of described one-level work molded lines and secondary work molded lines is the high-order moment curve.
7. two-stage rotary vane type expansion machine according to claim 6 is characterized in that: the easement curve of described one-level work molded lines and secondary work molded lines is continuous with working curve separately and sealing curve junction three order derivatives.
8. according to claim 1 or 6 or 7 described two-stage rotary vane type expansion machines, it is characterized in that: offer vane slot (11) on the described rotor (10), its incline direction is identical with the rotor direction of rotation, and the root size of vane slot is greater than the size of groove body.
9. two-stage rotary vane type expansion machine according to claim 8, it is characterized in that: described decompressor is except that air inlet (20) and gas outlet (14) and external communications, air inlet between all double expansions, exhaust passage all are arranged on decompressor inside, connect without exterior line.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009100214090A CN101504231B (en) | 2009-03-06 | 2009-03-06 | Two-stage rotary vane type expansion machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009100214090A CN101504231B (en) | 2009-03-06 | 2009-03-06 | Two-stage rotary vane type expansion machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101504231A CN101504231A (en) | 2009-08-12 |
| CN101504231B true CN101504231B (en) | 2010-11-10 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009100214090A Expired - Fee Related CN101504231B (en) | 2009-03-06 | 2009-03-06 | Two-stage rotary vane type expansion machine |
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Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103353192B (en) * | 2013-07-01 | 2016-03-02 | 新奥科技发展有限公司 | A kind of restriction expansion device and there is the refrigeration system of this device |
| CN105134299B (en) | 2015-07-21 | 2017-06-16 | 天津大学 | Suitable for two grades of double-work medium decompressors of organic Rankine bottoming cycle |
| CN112324512B (en) * | 2020-11-13 | 2021-08-31 | 珠海格力电器股份有限公司 | Symmetrical expansion machine |
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2009
- 2009-03-06 CN CN2009100214090A patent/CN101504231B/en not_active Expired - Fee Related
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Granted publication date: 20101110 Termination date: 20140306 |