CN103557158B - Coolant injection formula rotary compressor - Google Patents
Coolant injection formula rotary compressor Download PDFInfo
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- CN103557158B CN103557158B CN201310461632.3A CN201310461632A CN103557158B CN 103557158 B CN103557158 B CN 103557158B CN 201310461632 A CN201310461632 A CN 201310461632A CN 103557158 B CN103557158 B CN 103557158B
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Abstract
The present invention discloses a kind of coolant injection formula rotary compressor, comprising: housing, compression mechanism, spray tube and jet valve. Compression mechanism comprises: cylinder, main bearing babbitting jig, supplementary bearing, bent axle, piston and slide plate, the inwall of the cylinder chamber of cylinder is provided with filled mouth, and cylinder is provided with the filled passage with filling aperture. Closing condition it is in isolate filling aperture and filled mouth during the pressure that the pressure of jet valve in cylinder chamber is greater than in filling aperture, the state of opening it is in conducting filling aperture and filled mouth during the pressure that the pressure of jet valve in cylinder chamber is less than in filling aperture, it is in closing condition at jet valve, the space that can enter pressurized gas between jet valve and filled mouth is called the clearance volume that jet valve is formed, and the scope of the ratio between the clearance volume that jet valve is formed and cylinder aspirated volume is: 0.3%��1.5%. The coolant injection formula rotary compressor of the present invention, reduces the performance loss of coolant injection formula rotary compressor.
Description
Technical field
The present invention relates to compressor field, especially relate to a kind of coolant injection formula rotary compressor.
Background technology
The working process of general coolant injection formula rotary compressor is, when compressor air suction terminates, now the pressure in the compression chamber of compressor is lower than the pressure of coolant injection mouth, jet valve is unidirectional to be opened with jet flow stream in compression chamber, along with the motion of piston, the volume of compression chamber reduces gradually, and wherein gaseous tension raises gradually, when the pressure in compression chamber equals the pressure of coolant injection mouth, jet valve cuts out. Along with the further motion of piston, the volume of compression chamber reduces further, and when wherein gaseous tension is slightly higher than exhaust pressure, compressor exhaust valve is opened, and compressor starts is vented.
But common coolant injection formula rotary compressor exists following defect: due to the existence of jet valve and filled mouth, the high pressure gas being filled in jet valve gap and filled mouth will can not be further compressed discharge in piston motion to when filling mouth. The extra clearance volume of compressor will be become, it is referred to as the clearance volume that jet valve is formed, thus have impact on the performance of compressor. Simultaneously when piston motion is to filled mouth, the non-expellant gas of the positive compression possibility that also oriented suction muffler is revealed in compression chamber.
Summary of the invention
The present invention is intended to one of technical problem at least solving existence in prior art. For this reason, it is an object of the present invention to propose a kind of coolant injection formula rotary compressor reducing performance loss.
The coolant injection formula rotary compressor of embodiment, comprising: housing according to a first aspect of the present invention, compression mechanism, described compression mechanism is located in described housing, and described compression mechanism comprises: cylinder, and described cylinder is provided with cylinder chamber, vane slot and venting port, the inwall of described cylinder chamber is provided with filled mouth, and described cylinder is provided with the filled passage with filling aperture, main bearing babbitting jig, described main bearing babbitting jig is located at above described cylinder, supplementary bearing, described supplementary bearing is located at below described cylinder, bent axle, described bent axle runs through described main bearing babbitting jig, described cylinder chamber and described supplementary bearing, piston, described piston is located in described cylinder chamber rotationally and is enclosed within described bent axle outward, slide plate, described slide plate is located in described vane slot removablely and one end of described slide plate is stretched in described cylinder chamber with on the periphery being only against described piston, spray tube, described spray tube is inserted in described filled passage through described housing, jet valve, described jet valve is located on described cylinder, closing condition it is in isolate described filling aperture and described filled mouth during the pressure that the pressure of described jet valve in described cylinder chamber is greater than in described filling aperture, the state of opening it is in filling aperture described in conducting and described filled mouth during the pressure that the pressure of described jet valve in described cylinder chamber is less than in described filling aperture, wherein, it is in closing condition at described jet valve, the space that can enter pressurized gas between described jet valve and described filled mouth is called the clearance volume that described jet valve is formed, the scope of the ratio between the clearance volume that described jet valve is formed and described cylinder aspirated volume is: 0.3%��1.5%.
Coolant injection formula rotary compressor according to embodiments of the present invention, by making the scope of the ratio between clearance volume that jet valve formed and cylinder aspirated volume be: 0.3%��1.5%, thus the performance of coolant injection formula rotary compressor can be ensured, reduce the performance loss of coolant injection formula rotary compressor.
According to a particular embodiment of the invention, described jet valve comprises: spacing part, one end of described spacing part is fixed on described cylinder, is formed with gap between the other end of described spacing part and described cylinder, and described gap is becoming big gradually from described one end to the direction of the described the other end; Valve block, one end of described valve block is located between described spacing part and described cylinder, when pressure in described cylinder chamber is less than the pressure of described filling aperture, the other end of described valve block around described spacing part in described gap from level attitude away from described cylinder flexural deformation, make described filling aperture be connected with described filled mouth to open described filling aperture. Thus jet valve according to embodiments of the present invention has structure effective, the advantage that makes the efficiency of coolant injection formula rotary compressor high simple, reasonable in design, jet.
Further, described jet valve also comprises mounting block, described mounting block successively through described spacing part and described valve block so that described spacing part and described valve block are fixed on described cylinder. Thus it is convenient to the assembling of spacing part and valve block.
According to some embodiments of the present invention, at the lift H that valve block described in the central position of described filling aperture and the shortest distance between described spacing part are described valve block, the bending starting point of described valve block is described valve block bending length to the length of the central position of described filling aperture, described valve block meet H/L < 0.15 between lift H and valve block bending length L. Thus the bendability of valve block can be ensured, and make valve block not frangibility, it is to increase the reliability of jet valve.
In some embodiments of the invention, the angle that the line of the central point of described filled mouth and the central point of described cylinder and the medullary ray of described vane slot are formed is A, the angle that the line of the central point of described venting port and the central point of described cylinder and the medullary ray of described vane slot are formed is B, and described included angle A and described included angle B meet A��B+10 ��. Thus the position filling mouth is limited by the position of venting port, avoid filled mouth distance venting port too far away, and then at the end of avoiding exhaust, the refrigerant in compression chamber is too much back in suction muffler.
Specifically, the installation space for installing described jet valve is limited between the lower surface of described cylinder and the upper surface of described supplementary bearing.
The coolant injection formula rotary compressor of embodiment, comprising: housing according to a second aspect of the present invention, compression mechanism, described compression mechanism is located in described housing, described compression mechanism comprises: the first cylinder and the 2nd cylinder, described first cylinder and described 2nd cylinder are respectively equipped with cylinder chamber, vane slot and venting port, the inwall of cylinder chamber described in each is provided with filled mouth, and described first cylinder and described 2nd cylinder are respectively equipped with the filled passage with filling aperture, middle space bar, described middle space bar is located between described first cylinder and described 2nd cylinder, main bearing babbitting jig, described main bearing babbitting jig is located at above described first cylinder, supplementary bearing, described supplementary bearing is located at below described 2nd cylinder, bent axle, described bent axle runs through described main bearing babbitting jig, described middle space bar and described supplementary bearing, and described bent axle is arranged with two pistons, and described two pistons are located in the cylinder chamber of described first cylinder and described 2nd cylinder respectively, two slide plates, slide plate described in each is located in corresponding described vane slot removablely and one end of described slide plate is stretched in corresponding described cylinder chamber with on the periphery being only against corresponding described piston, two spray tubes, spray tube described in each is inserted in corresponding described filled passage through described housing, two jet valves, described two jet valves are located on described first cylinder and described 2nd cylinder respectively, closing condition it is in isolate described filling aperture and described filled mouth during the pressure that the pressure of jet valve described in each in corresponding described cylinder chamber is greater than in corresponding described filling aperture, the state of opening it is in filling aperture described in conducting and described filled mouth during the pressure that the pressure of jet valve described in each in corresponding described cylinder chamber is less than in corresponding described filling aperture, wherein, it is in closing condition at described two jet valves, the space sum that can enter pressurized gas between described two jet valves and corresponding described filled mouth is called the clearance volume that described two jet valves are formed, the scope of the ratio of the clearance volume that described two jet valves are formed and described first cylinder aspirated volume and described 2nd cylinder aspirated volume sum is: 0.3%��1.5%.
Coolant injection formula rotary compressor according to embodiments of the present invention, by making the scope of the ratio of clearance volume that jet valve formed and the first cylinder aspirated volume and the 2nd cylinder aspirated volume sum be: 0.3%��1.5%, thus the performance of coolant injection formula rotary compressor can be ensured, reduce the performance loss of coolant injection formula rotary compressor.
According to a particular embodiment of the invention, described in each, jet valve comprises: spacing part, one end of described spacing part is fixed on accordingly on described first cylinder or the 2nd cylinder, being formed with gap between the other end of described spacing part and corresponding described first cylinder or the 2nd cylinder, described gap is becoming big gradually from described one end to the direction of the described the other end; Valve block, one end of described valve block is located at described spacing part and accordingly between described first cylinder or the 2nd cylinder, when pressure in described cylinder chamber is less than the pressure of described filling aperture, the other end of described valve block around described spacing part in described gap from level attitude away from described first cylinder accordingly or the 2nd cylinder flexural deformation, make described filling aperture be connected with described filled mouth to open described filling aperture. Thus jet valve according to embodiments of the present invention has structure effective, the advantage that makes the efficiency of coolant injection formula rotary compressor high simple, reasonable in design, jet.
Further, jet valve described in each also comprises mounting block, described mounting block successively through described spacing part and described valve block described spacing part and described valve block are fixed on accordingly on described first cylinder or the 2nd cylinder. Thus the assembling of spacing part and valve block can be convenient to.
According to some embodiments of the present invention, in jet valve described in each, at the lift H that valve block described in the central position of described filling aperture and the shortest distance between described spacing part are described valve block, the bending starting point of described valve block is described valve block bending length to the length of the central position of described filling aperture, described valve block meet H/L < 0.15 between lift H and valve block bending length L. Thus the bendability of valve block can be ensured, and make valve block not frangibility, it is to increase the reliability of jet valve.
In some embodiments of the invention, the angle that the medullary ray of the line of the central point of the described filled mouth of described first cylinder and the central point of described first cylinder and the described vane slot of described first cylinder is formed is E, the angle that the medullary ray of the line of the central point of the described venting port of described first cylinder and the central point of described first cylinder and the described vane slot of described first cylinder is formed is F, and described angle E and described angle F meets E��F+10 ��. Thus limited the position of the filled mouth of the first cylinder by the position of the venting port on the first cylinder, and then at the end of avoiding exhaust, the refrigerant in the compression chamber of the first cylinder is too much back in the suction muffler of the first cylinder.
According to some embodiments of the present invention, the angle that the medullary ray of the line of the central point of the described filled mouth of described 2nd cylinder and the central point of described 2nd cylinder and the described vane slot of described 2nd cylinder is formed is G, the angle that the medullary ray of the line of the central point of the described venting port of described 2nd cylinder and the central point of described 2nd cylinder and the described vane slot of described 2nd cylinder is formed is K, and described angle G and described angle K meets G��K+10 ��. Thus limited the position of the filled mouth of the 2nd cylinder by the position of the venting port on the 2nd cylinder, and then at the end of avoiding exhaust, the refrigerant in the compression chamber of the 2nd cylinder is too much back in the suction muffler of the 2nd cylinder.
Specifically, between the lower surface of described first cylinder and the upper surface of described middle space bar, the installation space for installing described two jet valves is limited respectively between the upper surface of described 2nd cylinder and the lower surface of described middle space bar. Thus the structural compactness of coolant injection formula rotary compressor can be improved.
The additional aspect of the present invention and advantage will part provide in the following description, and part will become obvious from the following description, or be recognized by the practice of the present invention.
Accompanying drawing explanation
Above-mentioned and/or the additional aspect of the present invention and advantage from accompanying drawing below combining to the description of embodiment becoming obviously and it should be readily understood that wherein:
Fig. 1 is the schematic diagram of coolant injection formula rotary compressor according to an embodiment of the invention, comprising a cylinder;
Fig. 2 is the graph of a relation between the clearance volume of the jet valve formation of coolant injection formula rotary compressor according to embodiments of the present invention and compressor performance;
Fig. 3 is the schematic diagram of jet valve according to embodiments of the present invention when being located on described cylinder;
Fig. 4 is the top plan view of the cylinder being provided with piston, bent axle and slide plate according to embodiments of the present invention;
Fig. 5 is piston motion according to embodiments of the present invention to the edge of venting port and piston motion to schematic diagram when filling the edge of mouth;
Fig. 6 is the schematic diagram of coolant injection formula rotary compressor in accordance with another embodiment of the present invention, comprising the first cylinder and the 2nd cylinder.
Reference numeral:
Coolant injection formula rotary compressor 100, gas-liquid separator 200, housing 1,
Compression mechanism 2, cylinder 20, cylinder chamber 201, fill mouth 2011, compression chamber 2012,
Ventilative chamber 2013, vane slot 202, venting port 203, fill passage 204,
Filling aperture 2041, suction opening 205, main bearing babbitting jig 21, supplementary bearing 22, bent axle 23,
Piston 24, slide plate 25, spray tube 3, jet valve 4, spacing part 40, valve block 41,
Mounting block 42, gap 43, first cylinder 5, the 2nd cylinder 6, middle space bar 7
Embodiment
Being described below in detail embodiments of the invention, the example of described embodiment is shown in the drawings, and wherein same or similar label represents same or similar element or has element that is identical or similar functions from start to finish. It is exemplary below by the embodiment being described with reference to the drawings, only for explaining the present invention, and limitation of the present invention can not be interpreted as.
In describing the invention, it will be appreciated that, term " " center ", " longitudinal direction ", " transverse direction ", " on ", D score, " front ", " afterwards ", " left side ", " right side ", " vertically ", " level ", " top ", " end " " interior ", it is based on orientation shown in the drawings or position relation that the orientation of the instruction such as " outward " or position are closed, it is only the present invention for convenience of description and simplified characterization, instead of indicate or imply that the device referred to or element must have specific orientation, with specific orientation structure and operation, therefore limitation of the present invention can not be interpreted as. in addition, term " first ", " the 2nd " are only for describing object, and can not be interpreted as instruction or hint relative importance.
In describing the invention, it is necessary to explanation, unless otherwise clearly defined and limited, term " installation ", " being connected ", " connection " should be interpreted broadly, such as, it is possible to be fixedly connected with, it is also possible to be removably connect, or connect integratedly; Can be mechanically connected, it is also possible to be electrical connection; Can be directly be connected, it is also possible to be indirectly connected by intermediary, it is possible to be the connection of two element internals. For the ordinary skill in the art, it is possible to particular case understands above-mentioned term concrete implication in the present invention.
Coolant injection formula rotary compressor 100 can be applicable in the refrigeration systems such as conditioner, it is described by single cylinder and being applied in conditioner of coolant injection formula rotary compressor 100 below, conditioner comprises gas-liquid separator 200, the refrigerant entering it is separated refrigerant is separated into liquid refrigerants and gaseous coolant by gas-liquid separator 200, and gaseous coolant is sprayed into by spray tube 3 in the cylinder chamber 201 of cylinder 20. Coolant injection formula rotary compressor 100 is provided with jet valve 4, the inwall of cylinder chamber 201 is provided with filled mouth 2011, when jet valve 4 is opened, gaseous coolant is injected in the cylinder chamber 201 of cylinder 20 by filled mouth 2011, when jet valve 4 cuts out, the space that can enter pressurized gas between jet valve 4 and filled mouth 2011 is called the clearance volume that jet valve 4 is formed. Wherein, the structure of conditioner and principle of work etc., known by the technician of this area, are just not described in detail here.
Present inventor finds that the performance (COP) of compressor is had different impacts by the size of the clearance volume that jet valve 4 is formed, as shown in Figure 2, contriver equals 0.3% by the ratio found between the clearance volume that jet valve 4 is formed and cylinder 20 aspirated volume that a large amount of experiments is surprised, the performance of compressor is close to volume production performance level, reduce the clearance volume that jet valve 4 is formed again further, the performance of compressor is without obvious rising, the clearance volume that jet valve 4 less on the contrary is formed, bring the sharply decline of sharply rising and jet valve 4 reliability of jet valve 4 tooling cost, and the ratio between the clearance volume that jet valve 4 is formed and cylinder 20 aspirated volume is greater than 1.5%, the performance of compressor then sharply worsens. wherein, the method for calculation of the aspirated volume of cylinder 20 known by the technician of this area, are just not described in detail here. the application makes based on the discovery that contriver is above-mentioned.
Below with reference to Fig. 1-Fig. 5, coolant injection formula rotary compressor 100 according to an embodiment of the invention is described.
As Figure 1-Figure 5, coolant injection formula rotary compressor 100 according to embodiments of the present invention comprises: housing 1, compression mechanism 2, spray tube 3 and jet valve 4.
Compression mechanism 2 is located in housing 1, compression mechanism 2 comprises: cylinder 20, main bearing babbitting jig 21, supplementary bearing 22, bent axle 23, piston 24 and slide plate 25, wherein, cylinder 20 is provided with cylinder chamber 201, vane slot 202, venting port 203 and suction opening 205, the inwall of cylinder chamber 201 is provided with filled mouth 2011, cylinder 20 is provided with the filled passage 204 with filling aperture 2041, namely the one end filling passage 204 is filling aperture 2041, spray tube 3 is inserted in filled passage 204 through housing 1, and extraneous gaseous coolant is entered in filled passage 204 by spray tube 3. Main bearing babbitting jig 21 is located at above cylinder 20. Supplementary bearing 22 is located at below cylinder 20. Bent axle 23 runs through main bearing babbitting jig 21, cylinder chamber 201 and supplementary bearing 22, and the upper end on bent axle 23 is connected with motor with by 23 turns, driven by motor bent axle. Piston 24 is located in cylinder chamber 201 rotationally and is enclosed within bent axle 23 outward. Slide plate 25 is located in vane slot 202 removablely and one end of slide plate 25 is stretched in cylinder chamber 201 with on the periphery being only against piston 24.
As shown in Figure 4, bent axle 23 drives piston 24 to rotate, one end of slide plate 25 is only against on the periphery of piston 24, cylinder chamber 201 is divided into compression chamber 2012 and suction muffler 2013 by the piston 24 and the slide plate 25 that rotate, suction muffler 2013 is connected with suction opening 205, compression chamber 2012 is connected by vent valve 8 with venting port 203, along with the operation of coolant injection formula rotary compressor 100, the volume periodical change of compression chamber 2012 and suction muffler 2013, to complete air-breathing and compression process, wherein, what deserves to be explained is, main bearing babbitting jig 21 and supplementary bearing 22 also can be provided with sound damper, the principle of work of compression mechanism 2 is identical with the principle of work of the compression mechanism 2 in existing compressor, here just it is not described in detail.
Jet valve 4 is located on cylinder 20, it is in closing condition during the pressure that the pressure of jet valve 4 in cylinder chamber 201 is greater than in filling aperture 2041 to isolate filling aperture 2041 and filled mouth 2011, thus avoids the pressurized gas in cylinder chamber 201 to be back in filled passage 204. It is in, during the pressure that the pressure of jet valve 4 in cylinder chamber 201 is less than in filling aperture 2041, the state of opening, now jet valve 4 is opened with conducting filling aperture 2041 and filled mouth 2011, and gaseous coolant enters in cylinder chamber 201 through filling aperture 2041 and filled mouth 2011 successively. Wherein, it is in closing condition at jet valve 4, the space that can enter pressurized gas between jet valve 4 and filled mouth 2011 is called the clearance volume that jet valve 4 is formed, and the scope of the ratio between the clearance volume that jet valve 4 is formed and cylinder 20 aspirated volume is: 0.3%��1.5%.
Coolant injection formula rotary compressor 100 according to embodiments of the present invention, by making the scope of the ratio between clearance volume that jet valve 4 formed and cylinder 20 aspirated volume be: 0.3%��1.5%, thus the performance of coolant injection formula rotary compressor 100 can be ensured, reduce the performance loss of coolant injection formula rotary compressor 100.
Specifically, as shown in Figure 1, the installation space for installing jet valve 4 is limited between the lower surface of cylinder 20 and the upper surface of supplementary bearing 22. That is, the filling aperture 2041 filling passage 204 is positioned on the lower surface of cylinder 20, and jet valve 4 is located between the lower surface of cylinder 20 and the upper surface of supplementary bearing 22 for opening or closing filling aperture 2041. Certainly the present invention is not limited thereto, jet valve 4 also can be located between the upper surface of cylinder 20 and the lower surface of main bearing babbitting jig 21, and the filling aperture 2041 now filling passage 204 is positioned on the upper surface of cylinder 20.
As shown in figures 1 and 3, in a particular embodiment of the present invention, jet valve 4 comprises: spacing part 40 and valve block 41, wherein, one end of spacing part 40 is fixed on cylinder 20, being formed with gap 43 between the other end of spacing part 40 and cylinder 20, gap 43 becomes big gradually on the direction from one end to the other end. One end of valve block 41 is located between spacing part 40 and cylinder 20, when pressure in cylinder chamber 201 is less than the pressure of filling aperture 2041, the other end of valve block 41 around spacing part 40 in gap 43 from level attitude away from cylinder 20 flexural deformation, make filling aperture 2041 be connected with filled mouth 2011 to open filling aperture 2041, when pressure in cylinder chamber 201 is greater than the pressure of filling aperture 2041, namely the normality that valve block 41 is horizontal is not out of shape state to close filling aperture 2041. Thus jet valve 4 according to embodiments of the present invention has structure effective, the advantage that makes the efficiency of coolant injection formula rotary compressor 100 high simple, reasonable in design, jet.
In the example of the present invention, as shown in Figure 3, jet valve 4 is located on the lower surface of cylinder 20, now valve block 41 is deformable tabular body, the left end of valve block 41 is fixed on the lower surface of cylinder 20 so that valve block 41 is positioned at the lower section of filling aperture 2041, the left end of spacing part 40 is fixed on the lower surface of left end of valve block 41, limits gap 43 between the right-hand member of spacing part 40 and the lower surface of cylinder 20, and gap 43 increases in the left to right direction gradually. When now the pressure in cylinder chamber 201 is less than the pressure of filling aperture 2041, valve block 41 bends to open filling aperture 2041 downwards from level attitude in gap 43 around spacing part 40, when pressure in cylinder chamber 201 is greater than the pressure of filling aperture 2041, valve block 41 returns to level attitude to close filling aperture 2041.
When jet valve 4 is positioned at the upper surface of cylinder 20, now valve block 41 is located on the upper surface of cylinder 20 and valve block 41 is positioned at the top of filling aperture 2041, spacing part 40 is positioned at the top of valve block 41, when pressure in cylinder chamber 201 is less than the pressure of filling aperture 2041, valve block 41 is bent upwards from level attitude to open filling aperture 2041 around spacing part 40 in gap 43.
Further, jet valve 4 also comprises mounting block 42, mounting block 42 successively through spacing part 40 and valve block 41 so that spacing part 40 and valve block 41 are fixed on cylinder 20, that is, spacing part 40 and valve block 41 are fixed on cylinder 20 by mounting block 42, thus are convenient to the assembling of spacing part 40 and valve block 41. Specifically, mounting block 42 can be screw, and mounting block 42 can also be rivet.
As shown in Figure 3, in some embodiments of the invention, shortest distance between the central position valve block 41 and spacing part 40 of filling aperture 2041 is the lift H of valve block 41, the bending starting point of valve block 41 is valve block 41 bending length to the length of the central position of filling aperture 2041, valve block 41 meet H/L < 0.15 between lift H and valve block 41 bending length L. Thus it is less than 0.15 by being defined as by the ratio between the lift H of valve block 41 and valve block 41 bending length L, the bendability of valve block 41 can be ensured, and make valve block 41 not frangibility, it is to increase the reliability of jet valve 4.
According to some embodiments of the present invention, fill the line of central point of the central point of mouth 2011 and cylinder 20 and angle that the medullary ray of vane slot 202 is formed is A, the angle that the line of the central point of venting port 203 and the central point of cylinder 20 and the medullary ray of vane slot 202 are formed is that B, included angle A and included angle B meet A��B+10 ��. Thus the position filling mouth 2011 is limited by the position of venting port 203, avoid filled mouth 2011 too far away apart from venting port 203, and then at the end of avoiding exhaust, the refrigerant in compression chamber 2012 is too much back in suction muffler 2013.
In other embodiments of the present invention, as shown in Figure 5, also limit the position filling mouth 2011 with the position according to venting port 203 by such as under type, in the process that piston 24 moves, when the position, edge of periphery wall and filled mouth 2011 that piston 24 moves to piston 24 contact so that fill mouth 2011 be in suction muffler 2013 be not connected but when being about to the state of connection (as shown in solid lines in fig. 5), that is, when the periphery wall of piston 24 contacts with the position, edge of filled mouth 2011, as long as piston 24 continues to move, then filled mouth 2011 is connected with suction muffler 2013. the angle that now line of the central point of piston 24 central point and cylinder 20 and slide plate 25 direction of motion are formed is C.
Piston 24 continues motion, the position, edge of the periphery wall and venting port 203 that move to piston 24 when piston 24 contacts so that venting port 203 is in suction muffler 2013 and is not connected but is about to the state that is connected, that is, when the periphery wall of piston 24 contacts with the position, edge of venting port 203 (as shown in broken line in fig. 5), as long as piston 24 continues to move, venting port 203 is connected with suction muffler 2013. The angle that now line of the central point of piston 24 central point and cylinder 20 and slide plate 25 direction of motion are formed is D, and angle C and angle D meets C��D+10 ��.
Below with reference to Fig. 3-Fig. 6, coolant injection formula rotary compressor 100 in accordance with another embodiment of the present invention is described.
As shown in Figure 6, coolant injection formula rotary compressor 100 according to embodiments of the present invention comprises: housing 1, compression mechanism's 2, two spray tubes 3 and two jet valves 4, wherein compressing mechanism 2 is located in housing 1, it is outer to be connected with gas-liquid separator 200 that one end of each spray tube 3 is positioned at housing 1, and the other end of each spray tube 3 is positioned at housing 1.
Compression mechanism 2 comprises: the first cylinder 5 and the 2nd cylinder 6, middle space bar 7, main bearing babbitting jig 21, supplementary bearing 22, bent axle 23 and two slide plates 25, wherein, first cylinder 5 is positioned at the top of the 2nd cylinder 6, first cylinder 5 and the 2nd cylinder 6 are respectively equipped with cylinder chamber 201, vane slot 202, venting port 203 and suction opening 205, that is, first cylinder 5 is provided with cylinder chamber 201, vane slot 202, venting port 203 and suction opening 205, 2nd cylinder 6 is provided with cylinder chamber 201, vane slot 202, venting port 203 and suction opening 205, the inwall of each cylinder chamber 201 is provided with filled mouth 2011, first cylinder 5 and the 2nd cylinder 6 are respectively equipped with the filled passage 204 with filling aperture 2041, each spray tube 3 is inserted into corresponding filling in passage 204 through housing 1.
Middle space bar 7 is located between the first cylinder 5 and the 2nd cylinder 6. Main bearing babbitting jig 21 is located at above the first cylinder 5. Supplementary bearing 22 is located at below the 2nd cylinder 6. Bent axle 23 runs through main bearing babbitting jig 21, middle space bar 7 and supplementary bearing 22, bent axle 23 is arranged with two pistons 24, two pistons 24 are located in the cylinder chamber 201 of the first cylinder 5 and the 2nd cylinder 6 respectively, namely it is provided with in the cylinder chamber 201 of the first cylinder 5 in the cylinder chamber 201 of rotating piston the 24, two cylinder 6 and it is provided with rotating piston 24. Each slide plate 25 is located in corresponding vane slot 202 removablely and one end of slide plate 25 is stretched in corresponding cylinder chamber 201 with on the periphery being only against corresponding piston 24.
Bent axle 23 drives two pistons 24 to move in corresponding cylinder chamber 201 respectively, one end of each slide plate 25 is only against on the periphery wall of corresponding piston 24, the cylinder chamber 201 of the 2nd cylinder 6 is separated into compression chamber 2012 and suction muffler 2013 by the piston 24 of the motion that the cylinder chamber 201 of the first cylinder 5 is separated on compression chamber 2012 and suction muffler the 2013, two cylinder 6 by the piston 24 of the motion on the first cylinder 5 and slide plate 25 and slide plate 25. Wherein it should be noted that, the principle of work of the compression mechanism 2 of the present invention is identical with the principle of work of the compression mechanism 2 with two cylinder of the prior art, is just not described in detail here.
Two jet valves 4 are located on the first cylinder 5 and the 2nd cylinder 6 respectively, closing condition it is in isolate filling aperture 2041 and filled mouth 2011 during the pressure that the pressure of each jet valve 4 in corresponding cylinder chamber 201 is greater than in corresponding filling aperture 2041, the state of opening it is in conducting filling aperture 2041 and filled mouth 2011 during the pressure that the pressure of each jet valve 4 in corresponding cylinder chamber 201 is less than in corresponding filling aperture 2041, wherein, it is in closing condition at two jet valves 4, the space sum that can enter pressurized gas between two jet valves 4 and corresponding filled mouth 2011 is called the clearance volume that two jet valves 4 are formed, the scope of the clearance volume of two jet valve 4 formation and the ratio of the first cylinder 5 aspirated volume and the 2nd cylinder 6 aspirated volume sum is: 0.3%��1.5%.
Coolant injection formula rotary compressor 100 according to embodiments of the present invention, by making the scope of the ratio of clearance volume that jet valve 4 formed and the first cylinder 5 aspirated volume and the 2nd cylinder 6 aspirated volume sum be: 0.3%��1.5%, thus the performance of coolant injection formula rotary compressor 100 can be ensured, reduce the performance loss of coolant injection formula rotary compressor 100.
Specifically, between the lower surface of the first cylinder 5 and the upper surface of middle space bar 7, between the upper surface of the 2nd cylinder 6 and the lower surface of middle space bar 7, limit the installation space for installing two jet valves 4 respectively, that is, between the lower surface that jet valve 4 on first cylinder 5 is located at the first cylinder 5 and the upper surface of middle space bar 7, between the upper surface that the jet valve 4 on the 2nd cylinder 6 is located at the 2nd cylinder 6 and the lower surface of middle space bar 7. Thus the structural compactness of coolant injection formula rotary compressor 100 can be improved.
In some embodiments of the invention, as shown in Figure 3 and Figure 6, each jet valve 4 comprises: spacing part 40 and valve block 41, one end of spacing part 40 is fixed on corresponding first cylinder 5 or the 2nd cylinder 6, being formed with gap 43 between the other end of spacing part 40 and the first corresponding cylinder 5 or the 2nd cylinder 6, gap 43 becomes big gradually on the direction from one end to the other end. One end of valve block 41 is located between spacing part 40 and corresponding first cylinder 5 or the 2nd cylinder 6, when pressure in cylinder chamber 201 is less than the pressure of filling aperture 2041, the other end of valve block 41 around spacing part 40 in gap 43 from level attitude away from corresponding first cylinder 5 or the 2nd cylinder 6 flexural deformation, make filling aperture 2041 be connected with filled mouth 2011 to open filling aperture 2041, when pressure at cylinder chamber 201 is greater than the pressure of filling aperture 2041, valve block 41 is horizontal to close filling aperture 2041. Thus jet valve 4 according to embodiments of the present invention has structure effective, the advantage that makes the efficiency of coolant injection formula rotary compressor 100 high simple, reasonable in design, jet.
As shown in Figure 6, the position relation of the parts in jet valve 4 on the first cylinder 5 is as follows: the left end of valve block 41 is fixed on the lower surface of the first cylinder 5, the left end of spacing part 40 is fixed on the lower surface of valve block 41, limiting gap 43 between the right-hand member of spacing part 40 and the lower surface of the first cylinder 5, gap 43 increases in the left to right direction gradually. When now the pressure in the cylinder chamber 201 of the first cylinder 5 is less than the pressure of filling aperture 2041 of the first cylinder 5, valve block 41 bends to open filling aperture 2041 downwards from level attitude in gap 43 around spacing part 40, when pressure in the cylinder chamber 201 of the first cylinder 5 is greater than the pressure of filling aperture 2041 of the first cylinder 5, valve block 41 returns to level attitude to close filling aperture 2041.
The position relation of the parts in jet valve 4 on the 2nd cylinder 6 is as follows: the left end of valve block 41 is fixed on the upper surface of the 2nd cylinder 6, the left end of spacing part 40 is fixed on the upper surface of valve block 41, limiting gap 43 between the right-hand member of spacing part 40 and the upper surface of the 2nd cylinder 6, gap 43 increases in the left to right direction gradually. When now the pressure in the cylinder chamber 201 of the 2nd cylinder 6 is less than the pressure of filling aperture 2041 of the 2nd cylinder 6, valve block 41 is bent upwards from level attitude to open filling aperture 2041 around spacing part 40 in gap 43, when pressure in the cylinder chamber 201 of the 2nd cylinder 6 is greater than the pressure of filling aperture 2041 of the 2nd cylinder 6, valve block 41 returns to level attitude to close filling aperture 2041.
Further, each jet valve 4 also comprises mounting block 42, mounting block 42 successively through spacing part 40 and valve block 41 so that spacing part 40 and valve block 41 are fixed on corresponding first cylinder 5 or the 2nd cylinder 6. Thus the assembling of spacing part 40 and valve block 41 can be convenient to. Specifically, mounting block 42 can be screw, and mounting block 42 can also be rivet.
As shown in Figure 3, according to some embodiments of the present invention, in each jet valve 4, shortest distance between the central position valve block 41 and spacing part 40 of filling aperture 2041 is the lift H of valve block 41, the bending starting point of valve block 41 is valve block 41 bending length to the length of the central position of filling aperture 2041, valve block 41 meet H/L < 0.15 between lift H and valve block 41 bending length L. Specifically, the lift H of the valve block 41 in jet valve 4 on the first cylinder 5 refers to the distance between the lower surface of the central position valve block 41 of the filling aperture 2041 at the first cylinder 5 and the upper surface of spacing part 40, and the lift H of the valve block 41 in jet valve 4 on the 2nd cylinder 6 refers to the distance between the upper surface of the central position valve block 41 of the filling aperture 2041 at the 2nd cylinder 6 and spacing part 40. Thus it is less than 0.15 by being defined as by the ratio between the lift H of valve block 41 and valve block 41 bending length L, the bendability of valve block 41 can be ensured, and make valve block 41 not frangibility, it is to increase the reliability of jet valve 4.
In some embodiments of the invention, the angle that the medullary ray of the line of the central point of the filled mouth 2011 of the first cylinder 5 and the central point of the first cylinder 5 and the vane slot 202 of the first cylinder 5 is formed is E, the angle that the medullary ray of the line of the central point of the venting port 203 of the first cylinder 5 and the central point of the first cylinder 5 and the vane slot 202 of the first cylinder 5 is formed is F, and angle E and angle F meets E��F+10 ��. Thus limited the position of the filled mouth 2011 of the first cylinder 5 by the position of the venting port 203 on the first cylinder 5, and then at the end of avoiding exhaust, the refrigerant in the compression chamber 2012 of the first cylinder 5 is too much back in the suction muffler 2013 of the first cylinder 5.
Further, the angle that the medullary ray of the line of the central point of the filled mouth 2011 of the 2nd cylinder 6 and the central point of the 2nd cylinder 6 and the vane slot 202 of the 2nd cylinder 6 is formed is G, the angle that the medullary ray of the line of the central point of the venting port 203 of the 2nd cylinder 6 and the central point of the 2nd cylinder 6 and the vane slot 202 of the 2nd cylinder 6 is formed is K, and angle G and angle K meets G��K+10 ��. Thus limited the position of the filled mouth 2011 of the 2nd cylinder 6 by the position of the venting port 203 on the 2nd cylinder 6, and then at the end of avoiding exhaust, the refrigerant in the compression chamber 2012 of the 2nd cylinder 6 is too much back in the suction muffler 2013 of the 2nd cylinder 6.
Other formations of coolant injection formula rotary compressor 100 according to embodiments of the present invention and operation are all known for those of ordinary skills, are not described in detail here.
In the description of this specification sheets, at least one embodiment that the description of reference term " embodiment ", " some embodiments ", " illustrative examples ", " example ", " concrete example " or " some examples " etc. means to be contained in the present invention in conjunction with concrete feature, structure, material or feature that this embodiment or example describe or example. In this manual, the schematic representation of above-mentioned term is not necessarily referred to identical embodiment or example. And, the concrete feature of description, structure, material or feature can combine in an appropriate manner in any one or more embodiment or example.
Although it has been shown and described that embodiments of the invention, it will be understood by those skilled in the art that: these embodiments can be carried out multiple change, amendment, replacement and modification when not departing from principle and the objective of the present invention, the scope of the present invention by claim and etc. jljl limit.
Claims (11)
1. a coolant injection formula rotary compressor, it is characterised in that, comprising:
Housing;
Compression mechanism, described compression mechanism is located in described housing, and described compression mechanism comprises:
Cylinder, described cylinder is provided with cylinder chamber, vane slot and venting port, and the inwall of described cylinder chamber is provided with filled mouth, and described cylinder is provided with the filled passage with filling aperture;
Main bearing babbitting jig, described main bearing babbitting jig is located at above described cylinder;
Supplementary bearing, described supplementary bearing is located at below described cylinder;
Bent axle, described bent axle runs through described main bearing babbitting jig, described cylinder chamber and described supplementary bearing;
Piston, described piston is located in described cylinder chamber rotationally and is enclosed within described bent axle outward;
Slide plate, described slide plate is located in described vane slot removablely and one end of described slide plate is stretched in described cylinder chamber with on the periphery being only against described piston;
Spray tube, described spray tube is inserted in described filled passage through described housing;
Jet valve, described jet valve is located on described cylinder, closing condition it is in isolate described filling aperture and described filled mouth during the pressure that the pressure of described jet valve in described cylinder chamber is greater than in described filling aperture, the state of opening it is in filling aperture described in conducting and described filled mouth during the pressure that the pressure of described jet valve in described cylinder chamber is less than in described filling aperture, wherein, it is in closing condition at described jet valve, the space that can enter pressurized gas between described jet valve and described filled mouth is called the clearance volume that described jet valve is formed, the scope of the ratio between the clearance volume that described jet valve is formed and described cylinder aspirated volume is: 0.3%��1.5%,
The angle that the line of the central point of described filled mouth and the central point of described cylinder and the medullary ray of described vane slot are formed is A, the angle that the line of the central point of described venting port and the central point of described cylinder and the medullary ray of described vane slot are formed is B, and described included angle A and described included angle B meet A��B+10 ��.
2. coolant injection formula rotary compressor according to claim 1, it is characterised in that, described jet valve comprises:
Spacing part, one end of described spacing part is fixed on described cylinder, is formed with gap between the other end of described spacing part and described cylinder, and described gap is becoming big gradually from described one end to the direction of the described the other end;
Valve block, one end of described valve block is located between described spacing part and described cylinder, when pressure in described cylinder chamber is less than the pressure of described filling aperture, the other end of described valve block around described spacing part in described gap from level attitude away from described cylinder flexural deformation, make described filling aperture be connected with described filled mouth to open described filling aperture.
3. coolant injection formula rotary compressor according to claim 2, it is characterised in that, described jet valve also comprises mounting block, described mounting block successively through described spacing part and described valve block so that described spacing part and described valve block are fixed on described cylinder.
4. coolant injection formula rotary compressor according to claim 2, it is characterized in that, at the lift H that valve block described in the central position of described filling aperture and the shortest distance between described spacing part are described valve block, the bending starting point of described valve block is valve block bending length to the length of the central position of described filling aperture, described valve block meet H/L < 0.15 between lift H and valve block bending length L.
5. coolant injection formula rotary compressor according to any one of claim 1-4, it is characterised in that, limit the installation space for installing described jet valve between the lower surface of described cylinder and the upper surface of described supplementary bearing.
6. a coolant injection formula rotary compressor, it is characterised in that, comprising:
Housing;
Compression mechanism, described compression mechanism is located in described housing, and described compression mechanism comprises:
First cylinder and the 2nd cylinder, described first cylinder and described 2nd cylinder are respectively equipped with cylinder chamber, vane slot and venting port, the inwall of cylinder chamber described in each is provided with filled mouth, and described first cylinder and described 2nd cylinder are respectively equipped with the filled passage with filling aperture;
Middle space bar, described middle space bar is located between described first cylinder and described 2nd cylinder;
Main bearing babbitting jig, described main bearing babbitting jig is located at above described first cylinder;
Supplementary bearing, described supplementary bearing is located at below described 2nd cylinder;
Bent axle, described bent axle runs through described main bearing babbitting jig, described middle space bar and described supplementary bearing, and described bent axle is arranged with two pistons, and described two pistons are located in the cylinder chamber of described first cylinder and described 2nd cylinder respectively;
Two slide plates, slide plate described in each is located in corresponding described vane slot removablely and one end of described slide plate is stretched in corresponding described cylinder chamber with on the periphery being only against corresponding described piston;
Two spray tubes, spray tube described in each is inserted in corresponding described filled passage through described housing;
Two jet valves, described two jet valves are located on described first cylinder and described 2nd cylinder respectively, closing condition it is in isolate described filling aperture and described filled mouth during the pressure that the pressure of jet valve described in each in corresponding described cylinder chamber is greater than in corresponding described filling aperture, the state of opening it is in filling aperture described in conducting and described filled mouth during the pressure that the pressure of jet valve described in each in corresponding described cylinder chamber is less than in corresponding described filling aperture, wherein, it is in closing condition at described two jet valves, the space sum that can enter pressurized gas between described two jet valves and corresponding described filled mouth is called the clearance volume that described two jet valves are formed, the scope of the ratio of the clearance volume that described two jet valves are formed and described first cylinder aspirated volume and described 2nd cylinder aspirated volume sum is: 0.3%��1.5%,
The angle that the medullary ray of the line of the central point of the described filled mouth of described first cylinder and the central point of described first cylinder and the described vane slot of described first cylinder is formed is E, the angle that the medullary ray of the line of the central point of the described venting port of described first cylinder and the central point of described first cylinder and the described vane slot of described first cylinder is formed is F, and described angle E and described angle F meets E��F+10 ��.
7. coolant injection formula rotary compressor according to claim 6, it is characterised in that, described in each, jet valve comprises:
Spacing part, one end of described spacing part is fixed on accordingly on described first cylinder or the 2nd cylinder, being formed with gap between the other end of described spacing part and corresponding described first cylinder or the 2nd cylinder, described gap is becoming big gradually from described one end to the direction of the described the other end;
Valve block, one end of described valve block is located at described spacing part and accordingly between described first cylinder or the 2nd cylinder, when pressure in described cylinder chamber is less than the pressure of described filling aperture, the other end of described valve block around described spacing part in described gap from level attitude away from described first cylinder accordingly or the 2nd cylinder flexural deformation, make described filling aperture be connected with described filled mouth to open described filling aperture.
8. coolant injection formula rotary compressor according to claim 7, it is characterized in that, jet valve described in each also comprises mounting block, described mounting block successively through described spacing part and described valve block described spacing part and described valve block are fixed on accordingly on described first cylinder or the 2nd cylinder.
9. coolant injection formula rotary compressor according to claim 7, it is characterized in that, in jet valve described in each, at the lift H that valve block described in the central position of described filling aperture and the shortest distance between described spacing part are described valve block, the bending starting point of described valve block is valve block bending length to the length of the central position of described filling aperture, described valve block meet H/L < 0.15 between lift H and valve block bending length L.
10. coolant injection formula rotary compressor according to claim 6, it is characterized in that, the angle that the medullary ray of the line of the central point of the described filled mouth of described 2nd cylinder and the central point of described 2nd cylinder and the described vane slot of described 2nd cylinder is formed is G, the angle that the medullary ray of the line of the central point of the described venting port of described 2nd cylinder and the central point of described 2nd cylinder and the described vane slot of described 2nd cylinder is formed is K, and described angle G and described angle H meets G��K+10 ��.
The 11. coolant injection formula rotary compressors according to any one of claim 6-10, it is characterized in that, between the lower surface of described first cylinder and the upper surface of described middle space bar, between the upper surface of described 2nd cylinder and the lower surface of described middle space bar, limit the installation space for installing described two jet valves respectively.
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| CN105423664B (en) * | 2014-09-12 | 2017-12-29 | 上海日立电器有限公司 | Coolant injection device and rotary compressor |
| CN105402128A (en) * | 2014-09-12 | 2016-03-16 | 上海日立电器有限公司 | Rotary compressor cylinder structure and air-conditioning system |
| CN104791251B (en) * | 2015-04-16 | 2018-07-17 | 广东美芝制冷设备有限公司 | Rotary compressor and the heat pump system with it, air-conditioning system |
| CN105114310B (en) * | 2015-08-21 | 2019-08-02 | 广东美芝制冷设备有限公司 | Rotary compressor and its compression assembly |
| CN105422462B (en) * | 2015-12-10 | 2018-04-10 | 安徽美芝精密制造有限公司 | Rotary positive displacement compressor |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2490332Y (en) * | 2001-07-17 | 2002-05-08 | 江苏白雪电器股份有限公司 | Suction-exhaust mechanism of cylinder for compressor |
| CN101624985A (en) * | 2009-07-24 | 2010-01-13 | 广东美芝制冷设备有限公司 | Gas coolant injection rotary compressor |
| CN202132235U (en) * | 2011-06-21 | 2012-02-01 | 广东美芝制冷设备有限公司 | Air refrigerant ejecting rotary type compressor |
| CN202301033U (en) * | 2011-09-30 | 2012-07-04 | 广东美芝制冷设备有限公司 | Refrigerant injection rotary compressor |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0337391A (en) * | 1989-07-04 | 1991-02-18 | Hitachi Ltd | Rotary compressor |
| JP3979407B2 (en) * | 2004-08-23 | 2007-09-19 | ダイキン工業株式会社 | Rotary compressor |
-
2013
- 2013-09-30 CN CN201310461632.3A patent/CN103557158B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2490332Y (en) * | 2001-07-17 | 2002-05-08 | 江苏白雪电器股份有限公司 | Suction-exhaust mechanism of cylinder for compressor |
| CN101624985A (en) * | 2009-07-24 | 2010-01-13 | 广东美芝制冷设备有限公司 | Gas coolant injection rotary compressor |
| CN202132235U (en) * | 2011-06-21 | 2012-02-01 | 广东美芝制冷设备有限公司 | Air refrigerant ejecting rotary type compressor |
| CN202301033U (en) * | 2011-09-30 | 2012-07-04 | 广东美芝制冷设备有限公司 | Refrigerant injection rotary compressor |
Non-Patent Citations (1)
| Title |
|---|
| "通过减小余隙容积提高压缩机COP值";杨任平;《家电科技》;20111231(第12期);第1-7段及表1-2 * |
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Inventor after: Yang Guoyong Inventor after: Zheng Liyu Inventor after: Zhang Cheng Inventor after: Yu Yangbo Inventor before: Yang Guoyong |
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