CN204755311U - Rotary compressor and heat pump system , air conditioning system that have it - Google Patents
Rotary compressor and heat pump system , air conditioning system that have it Download PDFInfo
- Publication number
- CN204755311U CN204755311U CN201520232718.3U CN201520232718U CN204755311U CN 204755311 U CN204755311 U CN 204755311U CN 201520232718 U CN201520232718 U CN 201520232718U CN 204755311 U CN204755311 U CN 204755311U
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- cylinder
- rotary compressor
- compression chamber
- injection
- injection channel
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Abstract
The utility model discloses a rotary compressor and heat pump system, air conditioning system that have it, rotary compressor includes: a housing, compressing mechanism and injection valve, the compressing mechanism includes the base bearing, cylinder components, supplementary bearing and piston, the axial both ends at cylinder components are established respectively to base bearing and supplementary bearing, cylinder components includes the cylinder, the cylinder has the compression chamber, be formed with the cylinder gas vent on the cylinder, be formed with injection channel on the compressing mechanism, injection channel is used for letting in the injection refrigerant to the compression intracavity, the pressure that sprays the refrigerant is greater than the pressure and be lighter than the discharge pressure of cylinder of breathing in of cylinder, injection channel's minimum cross -sectional area is S1 (mm2), the swept volume of cylinder is V1 (mm3), S1V1 satisfies: 0.08 per mill (mm -1) S1V1 <= 1.2 per mill (mm -1), switching on and cutting off with control injection channel and compression chamber on the compressing mechanism is established to the injection valve. According to the utility model discloses a rotary compressor can guarantee rotary compressor's ability and efficiency.
Description
Technical field
The utility model relates to Compressor Manufacturing technical field, especially relates to a kind of rotary compressor and has its heat pump, air-conditioning system.
Background technique
Point out in correlation technique, the emitted dose Flow area of rotary air injection enthalpy-increasing compressor is too small, rotary air injection enthalpy-increasing compressor capacity can be caused not enough, cannot meet user's requirement; If jetburner is excessive, then can cause easy blowing zone liquid in certain environments, affect compressor efficiency, and the vibration of rotary air injection enthalpy-increasing compressor on low frequency and noise also may be caused to have larger deterioration, even can produce the noise that abnormal slide plate clashes into.In addition, be directly injected in the compression chamber of rotary air injection enthalpy-increasing compressor owing to spraying refrigerant, if blowing zone liquid, its hazard ratio absorbing gas belt liquid is even more serious, jet liquid-storage container design is unreasonable, be then easy to cause blowing zone liquid, thus affect the reliability of rotary air injection enthalpy-increasing compressor.
Model utility content
The utility model is intended at least to solve one of technical problem existed in prior art.For this reason, an object of the present utility model is to propose a kind of rotary compressor, can ensure ability and the efficiency of described rotary compressor.
Another object of the present utility model is to propose a kind of heat pump with above-mentioned rotary compressor.
Another object of the present utility model is to propose a kind of air-conditioning system with above-mentioned rotary compressor.
According to the rotary compressor of the utility model first aspect, comprising: housing, compressing mechanism, described compressing mechanism comprises main bearing, cylinder assembly, supplementary bearing and piston, described main bearing and described supplementary bearing are located at the axial two ends of described cylinder assembly respectively, described cylinder assembly comprises cylinder, described cylinder has compression chamber, described piston is located in described compression chamber and inwall along described compression chamber can roll, described cylinder is formed with cylinder exhaust port, described compressing mechanism is formed with injection channel, described injection channel is used for passing into injection refrigerant in described compression chamber, the pressure of described injection refrigerant is greater than the pressure of inspiration(Pi) of described cylinder, and be less than the exhaust pressure of described cylinder, the smallest cross-section area of wherein said injection channel is S
1(mm
2), the swept volume of described cylinder is V
1(mm
3), described S
1/ V
1meet: 0.08 ‰ (mm
-1)≤S
1/ V
1≤ 1.2 ‰ (mm
-1), and injection valve, described injection valve is located on described compressing mechanism to control conducting and the partition of described injection channel and described compression chamber.
According to rotary compressor of the present utility model, by by S
1/ V
1be set to satisfied 0.08 ‰ (mm
-1)≤S
1/ V
1≤ 1.2 ‰ (mm
-1), ability and the efficiency of rotary compressor can be ensured.
Alternatively, described injection channel comprises: spray valve seat, described injection valve seat is formed on the end face of described cylinder, the inwall of described injection valve seat is formed with jetburner, described injection refrigerant passes in described compression chamber by described jetburner, wherein said injection valve is located to open and close described jetburner on described injection valve seat, and described injection valve is configured to open described jetburner when the pressure in described compression chamber is less than the pressure at described jetburner place, cut out described jetburner when the pressure in described compression chamber is greater than the pressure at described jetburner place; And communicating passage, described communicating passage is located between described injection valve seat and described compression chamber to be communicated with described injection valve seat and described compression chamber.
Further alternatively, described S
1/ V
1meet: 0.6 ‰ (mm
-1)≤S
1/ V
1≤ 1.2 ‰ (mm
-1).
Further alternatively, the head of described injection valve seat is formed with circular receiving cavity, and described jetburner is formed on the inwall of described circular receiving cavity, and the radius of wherein said circular receiving cavity is R
1(mm), the radius of described compression chamber is R
2(mm), the distance between the center of described circular receiving cavity and the center of described compression chamber is L (mm), wherein said R
1, R
2, L meet: L=R
1+ R
2+ (0.2 ~ 0.7) mm.
Alternatively, the degree of depth of described communicating passage is h
1, the degree of depth of described circular receiving cavity is h
2, wherein said h
1, h
2meet: h
2=h
1+ (0.1 ~ 0.5) mm.
Alternatively, the Extreme breadth of described communicating passage is d
1, the Extreme breadth of described cylinder exhaust port is d
2, wherein d
1/ d
2meet: 0.4≤d
1/ d
2≤ 1.2.
Further alternatively, described d
1/ d
2meet further: 0.8≤d
1/ d
2≤ 1.0.
Or alternatively, described injection channel is formed at least one in described main bearing and described supplementary bearing, at least one the side end face of the described cylinder of vicinity described in described main bearing and described supplementary bearing is run through in one end of described injection channel, and wherein said injection valve is described piston.
Further alternatively, described S
1/ V
1meet: 0.08 ‰ (mm
-1)≤S
1/ V
1≤ 0.6 ‰ (mm
-1).
Further, described rotary compressor comprises further: jet liquid-storage container, and described jet liquid-storage container is located at outside described housing, and described jet liquid-storage container is connected to pass into described injection refrigerant in described injection channel with described injection channel.
Alternatively, described cylinder assembly comprises a described cylinder, and effective liquid storage volume of described jet liquid-storage container is V
2, wherein said V
2/ V
1meet: 1.5≤V
2/ V
1≤ 4.
Further alternatively, described V
2/ V
1meet further: 1.9≤V
2/ V
1≤ 2.8.
Alternatively, described cylinder assembly comprises multiple described cylinder, and effective liquid storage volume of described jet liquid-storage container is V
2, the swept volume sum of described multiple cylinder is V
1', wherein said V
2/ V
1' meet: 1.2≤V
2/ V
1'≤3.
Further alternatively, described V
2/ V
1' meet further: 1.5≤V
2/ V
1'≤2.2.
Particularly, described jet liquid-storage container comprises: shell, described shell is formed with import and outlet; With go out pipe, described go out one end of pipe stretch in described shell through described outlet, described go out described one end of pipe close, and described in go out described one end of pipe sidewall on be formed with at least one side direction vent, wherein said go out the other end of pipe be communicated with described injection channel.
Alternatively, described side direction vent for multiple and described multiple side direction vent along described in go out the circumference of pipe symmetrical.
Alternatively, the number of described side direction vent is 4 ~ 10.
Alternatively, the area sum of at least one side direction vent described is S
2, wherein said S
2/ S
1meet: 1≤S
2/ S
1≤ 4.
Alternatively, the area sum of at least one side direction vent described is S
2, described in go out pipe for pipe, and described in go out pipe smallest cross-section area be S
3, wherein said S
2/ S
3meet: 0.5≤S
2/ S
3≤ 1.3.
Further, described jet liquid-storage container also comprises: net-filter assembly, and described net-filter assembly to be located in described shell and to go out described one end of pipe described in being positioned at.
According to the heat pump of the utility model second aspect, comprising: according to the rotary compressor of the above-mentioned first aspect of the utility model; Two heat exchangers, the one end of one of them in described two heat exchangers is connected with the intakeport of described rotary compressor, and another the one end in described two heat exchangers is connected with the relief opening of described rotary compressor; Two throttling arrangements, described two throttling arrangements are located between the other end of described two heat exchangers; And flash vessel, described flash vessel is located between described two throttling arrangements, and wherein said flash vessel is communicated with to pass into described injection refrigerant in described injection channel with described injection channel.
According to the air-conditioning system of the utility model third aspect, comprising: according to the rotary compressor of the above-mentioned first aspect of the utility model; Two heat exchangers, the one end of one of them in described two heat exchangers is connected with the intakeport of described rotary compressor, and another the one end in described two heat exchangers is connected with the relief opening of described rotary compressor; Two throttling arrangements, described two throttling arrangements are located between the other end of described two heat exchangers; And flash vessel, described flash vessel is located between described two throttling arrangements, and wherein said flash vessel is communicated with to pass into described injection refrigerant in described injection channel with described injection channel.
Additional aspect of the present utility model and advantage will part provide in the following description, and part will become obvious from the following description, or be recognized by practice of the present utility model.
Accompanying drawing explanation
Above-mentioned and/or additional aspect of the present utility model and advantage will become obvious and easy understand from accompanying drawing below combining to the description of embodiment, wherein:
Fig. 1 is the schematic diagram of the rotary compressor according to the utility model embodiment;
Fig. 2 is the plan view of the cylinder shown in Fig. 1;
Fig. 3 is the worm's eye view of the cylinder shown in Fig. 1;
Fig. 4 is the enlarged view in the A portion that Fig. 3 centre circle shows;
Fig. 5 is the sectional drawing along B-B line in Fig. 3;
Fig. 6 is the sectional drawing along C-C line in Fig. 3;
Fig. 7 is that the COP (CoefficientOfPerformance, the coefficient of performance) of rotary compressor according to the utility model embodiment is with S
1/ V
1change schematic diagram;
Fig. 8 is with S according to the refrigerating capacity of the heat pump of the utility model embodiment
1/ V
1change schematic diagram;
Fig. 9 is with V according to the COP of the rotary compressor of the utility model embodiment
2/ V
1change schematic diagram;
Figure 10 is with V according to the swept volume liquid content of the jet liquid-storage container of the utility model embodiment
2/ V
1change schematic diagram;
Figure 11 is with d according to the refrigerating capacity of the heat pump of the utility model embodiment and power
1/ d
2change schematic diagram, wherein top is refrigerating capacity, below be power;
Figure 12 is the schematic diagram of main bearing according to the utility model embodiment or supplementary bearing;
Figure 13 is the schematic diagram of the jet liquid-storage container according to the utility model embodiment;
Figure 14 is another schematic diagram of the jet liquid-storage container according to the utility model embodiment;
Figure 15 is the schematic diagram of the heat pump according to the utility model embodiment.
Reference character:
100: rotary compressor;
1: housing; 11: relief opening;
21: main bearing; 22: cylinder; 221: compression chamber; 222: vane slot; 223: cylinder exhaust port;
224: cylinder intakeport; 225: spray valve seat; 226: jetburner; 227: circular receiving cavity;
228: communicating passage; Fill passage at 2291: the first; Fill passage at 2292: the second;
23: supplementary bearing; 24: piston; 25: motor;
3: jet liquid-storage container; 31: shell; 32: go out pipe; 33: net-filter assembly;
311: import; 321: side direction vent;
4: air-breathing liquid-storage container; 41: intakeport;
200: heat pump; 201: heat exchanger; 202: throttling arrangement; 203: flash vessel; 204: four-way valve.
Embodiment
Be described below in detail embodiment of the present utility model, 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.Being exemplary below by the embodiment be described with reference to the drawings, only for explaining the utility model, and can not being interpreted as restriction of the present utility model.
In description of the present utility model, it will be appreciated that, term " " center ", " transverse direction ", " length ", " width ", " thickness ", " on ", D score, " front ", " afterwards ", " left side ", " right side ", " vertically ", " level ", " top ", " end ", " interior ", " outward ", " axis ", " radial direction ", orientation or the position relationship of the instruction such as " circumference " are based on orientation shown in the drawings or position relationship, only the utility model and simplified characterization for convenience of description, instead of indicate or imply that the device of indication or element must have specific orientation, with specific azimuth configuration and operation, therefore can not be interpreted as restriction of the present utility model.
In addition, term " first ", " second " only for describing object, and can not be interpreted as instruction or hint relative importance or imply the quantity indicating indicated technical characteristics.Thus, be limited with " first ", the feature of " second " can express or impliedly comprise one or more these features.In description of the present utility model, except as otherwise noted, the implication of " multiple " is two or more.
In description of the present utility model, it should be noted that, unless otherwise clearly defined and limited, term " installation ", " being connected ", " connection " should be interpreted broadly, and such as, can be fixedly connected with, also can be removably connect, or connect integratedly; Can be directly be connected, also indirectly can be connected by intermediary, can be the connection of two element internals.For the ordinary skill in the art, concrete condition the concrete meaning of above-mentioned term in the utility model can be understood.
Below with reference to Fig. 1-Figure 15, the rotary compressor 100 according to the utility model embodiment is described.Wherein, rotary compression thermomechanical components 100 can be applied in heat pump 200, but is not limited thereto.
As shown in Figure 1, according to the rotary compressor 100 of the utility model first aspect embodiment, housing 1, compressing mechanism and injection valve is comprised.
Rotary compressor 100 can be vertical compressor.In description below the application, be described for vertical compressor for rotary compressor 100.Certainly, those skilled in the art are appreciated that rotary compressor 100 can also be horizontal compressor (scheming not shown).Here, it should be noted that, " vertical compressor " can be understood as the central axis upright of the cylinder 22 of the compressing mechanism of rotary compressor 100 in the compressor of the attachment face of rotary compressor 100, such as, as shown in Figure 1, the central axis of cylinder 22 vertically extends.Correspondingly, the central axis that " horizontal compressor " can be understood as cylinder 22 is roughly parallel to the compressor of the attachment face of rotary compressor 100.
Rotary compressor 100 also comprises motor 25, and with reference to Fig. 1, housing 1 is vertically arranged, now the central axis of housing 1 vertically extends.Housing 1 is preferably formed to rotary structure, to facilitate manufacturing.Motor 25 and compressing mechanism are all located in housing 1, and motor 25 and compressing mechanism are arranged in the vertical direction, and motor 25 is positioned at the top of compressing mechanism, and motor 25 is connected to compress the refrigerant entered in it with compressing mechanism.
Specifically, compressing mechanism comprises main bearing 21, cylinder assembly, supplementary bearing 23 and piston 24, main bearing 21 and supplementary bearing 23 are located at the axial two ends of cylinder assembly respectively, when rotary compressor 100 is vertical compressor, main bearing 21 and supplementary bearing 23 are located at the top and bottom of cylinder assembly respectively, as shown in Figure 1.
When rotary compressor 100 is single cylinder compressor, with reference to Fig. 1 composition graphs 2, cylinder assembly comprises a cylinder 22, the vane slot 222 that cylinder 22 has compression chamber 221 and is communicated with compression chamber 221, piston 24 is provided with in compression chamber 221, piston 24 can roll along the inwall of compression chamber 221, vane slot 222 extends along the radial direction of cylinder 22, slide plate is provided with in vane slot 222, slide plate removable and the inner of slide plate and piston 24 periphery wall in vane slot 222 only supports, cylinder 22 is formed with cylinder intakeport 224 and cylinder exhaust port 223, cylinder intakeport 224 is for being passed in compression chamber 221 by refrigerant to be compressed, cylinder exhaust port 223 is for discharging the refrigerant after compression outside cylinder 22.Here, it should be noted that, direction " interior " can be understood as towards the direction at cylinder 22 center, and its opposite direction is defined as " outward ", namely away from the direction at cylinder 22 center.
When rotary compressor 100 is for multicylinder compressor (scheming not shown), cylinder assembly comprises multiple cylinder 22, multiple cylinder 22 is arranged in the axial direction, dividing plate is provided with between two often adjacent cylinders 22, the vane slot 222 that each cylinder 22 all has compression chamber 221 and is communicated with compression chamber 221, be equipped with piston 24 in each compression chamber 221, and be equipped with slide plate in each vane slot 222.Be appreciated that other formation of multicylinder compressor is substantially identical with single cylinder compressor, do not repeat them here.
Compressing mechanism is formed with injection channel, and injection channel is used for passing into injection refrigerant in compression chamber 221.Spray the pressure of refrigerant and be greater than the pressure of inspiration(Pi) of cylinder 22 and the pressure spraying refrigerant is less than the exhaust pressure of cylinder 22.That is, spray the pressure of refrigerant and be greater than the pressure of the refrigerant to be compressed sucked from cylinder intakeport 224 and the pressure spraying refrigerant is less than the pressure of the refrigerant after the compression of discharging from cylinder exhaust port 223.Injection valve is located on compressing mechanism to control conducting and the partition of injection channel and compression chamber 221.
This rotary compressor 100 with injection channel is mainly in order to increase the ability of rotary compressor 100, heating capacity particularly under cryogenic conditions, its general working procedure is: when rotary compressor 100 air-breathing terminates, pressure now in compression chamber 221 is lower than the pressure in refrigerant passage, injection valve is opened, injection refrigerant is sprayed in compression chamber 221, along with the motion of piston 24, the volume of compression chamber 221 reduces gradually, in compression chamber 221, gas pressure raises gradually, when equaling the pressure in refrigerant passage when the pressure in compression chamber 221, injection valve cuts out.Along with the further motion of piston 24, the volume of compression chamber 221 reduces further, and when the exhaust pressure of a little higher than cylinder 22 of the gas pressure in compression chamber 221, the outlet valve of rotary compressor 100 is opened, and rotary compressor 100 starts exhaust.
Wherein, the smallest cross-section area of injection channel is S
1(mm
2), the swept volume of cylinder 22 is V
1(mm
3), S
1/ V
1meet: 0.08 ‰ (mm
-1)≤S
1/ V
1≤ 1.2 ‰ (mm
-1).Here, it should be noted that, " swept volume of cylinder 22 " can be understood as piston 24 and is moving to the inswept volume that to move between another stop from a stop.Be appreciated that S
1/ V
1concrete numerical value can according to actual requirement adaptive change, the utility model does not do concrete restriction to this.
According to the rotary compressor 100 of the utility model embodiment, by by S
1/ V
1be set to satisfied 0.08 ‰ (mm
-1)≤S
1/ V
1≤ 1.2 ‰ (mm
-1), ability and the efficiency of rotary compressor 100 can be ensured.
According to an embodiment of the present utility model, with reference to Fig. 3 composition graphs 4, injection channel comprises: spray valve seat 225 and communicating passage 228, spraying valve seat 225 is formed on the end face of cylinder 22, such as, spraying valve seat 225 can be formed on the upper-end surface of cylinder 22, also can be formed on the lower end surface of cylinder 22, and spraying valve seat 225 can be formed by the corresponding end-faces of cylinder 22 is recessed towards the other end of cylinder 22.Wherein, spraying valve seat 225 can depart from (as shown in Figure 3) relative to the radial direction edge of cylinder 22 from inside to outside counterclockwise, and certainly, spraying valve seat 225 can also depart from relative to the radial direction edge of cylinder 22 from inside to outside clockwise.
As shown in Figure 3, cylinder intakeport 224 is positioned at the side (such as, the right side in Fig. 3) of vane slot 222, sprays the opposite side (left side such as, in Fig. 3) that valve seat 225 is positioned at vane slot 222.
Further, cylinder 22 is formed with filled passage, the one end filling passage is communicated with jetburner 226, the other end runs through the periphery wall of cylinder 22, specifically, with reference to Fig. 5 and Fig. 6, filled passage comprises first and fills passage 2291 and the second filled passage 2292, first fills passage 2291 vertically extends, first upper end filling passage 2291 is communicated with jetburner 226, second fills passage 2292 extends along inward-outward direction, second the inner filling passage 2292 is communicated with the first lower end filling passage 2291, the periphery wall of cylinder 22 is run through in second outer end filling passage 2292, thus injection refrigerant can flow through the second filled passage 2292 successively, jetburner 226 is flowed to after first filled passage 2291.
The inwall of injection valve seat 225 is formed with jetburner 226, such as, as shown in Figure 3 and Figure 4, when spraying valve seat 225 and being formed on the lower end surface of cylinder 22, jetburner 226 can be formed on the roof of injection valve seat 225, and jetburner 226 is positioned at the one end of the contiguous compression chamber 221 spraying valve seat 225.Spray refrigerant to be passed in compression chamber 221 by jetburner 226.
Wherein, injection valve is located at and sprays on valve seat 225 to open and close jetburner 226, specifically, one end of injection valve can connect (such as screw connection) in injection valve seat 225, the other end of injection valve covers on jetburner 226, and injection valve is configured to open jetburner 226 when the pressure in compression chamber 221 is less than the pressure at jetburner 226 place, cuts out jetburner 226 when the pressure in compression chamber 221 is greater than the pressure at jetburner 226 place.In other words, when the pressure in compression chamber 221 is less than the pressure in filled passage, injection valve is in open mode with conducting jetburner 226 and compression chamber 221, and when the pressure in compression chamber 221 is greater than the pressure in filled passage, injection valve is in closed condition to isolate jetburner 226 and compression chamber 221.
When rotary compressor 100 is applied in heat pump 200, filled passage can be connected with the flash vessel 203 in heat pump 200, and now injection refrigerant can be the refrigerant after flash vessel 203 shwoot.
Communicating passage 228 is located to spray between valve seat 225 and compression chamber 221 sprays valve seat 225 and compression chamber 221 to be communicated with, as shown in Figure 4 and Figure 5, communicating passage 228 is located on the same end face of cylinder 22 together with injection valve seat 225, communicating passage 228 can be formed towards another end face of cylinder 22 is recessed by the corresponding end-faces of cylinder 22, specifically, one end of communicating passage 228 is communicated with injection valve seat 225, and the other end of communicating passage 228 is communicated with compression chamber 221.When jetburner 226 opened by injection valve, the injection refrigerant filled in passage can flow through communicating passage 228 by jetburner 226 and enter in compression chamber 221.
Alternatively, S
1/ V
1meet: 0.6 ‰ (mm
-1)≤S
1/ V
1≤ 1.2 ‰ (mm
-1).When rotary compressor 100 is applied in heat pump 200, such as, as shown in figure 15, refrigerant is pressed to be gas-liquid mixed two-phase flow state in after one of them throttling in two throttling arrangements 202, part gaseous coolant enters in housing 1 by flash vessel 203 from jetburner 226, remaining refrigerant, then after another throttling in two throttling arrangements 202 becomes low pressure, enters heat exchanger 201 such as vaporizer, then gets back in housing 1 from the intakeport 41 of rotary compressor 100.
By by S
1/ V
1be set to satisfied 0.6 ‰ (mm
-1)≤S
1/ V
1≤ 1.2 ‰ (mm
-1), injection channel there will not be the phenomenon of jet band liquid, and the coolant quantity entering into heat exchanger 201 such as vaporizer is comparatively large, can promote the refrigerating capacity of rotary compressor 100 like this.In addition, there will not be when low frequency excessive compression chamber 221 internal pressure that causes of emitted dose to fluctuate greatly, the phenomenon of disengaging may be produced between slide plate and piston 24, and then cause the generation of strike note.Generally speaking, by by S
1/ V
1be set to satisfied 0.6 ‰ (mm
-1)≤S
1/ V
1≤ 1.2 ‰ (mm
-1), can ensure refrigerating capacity and/or the heating capacity of heat pump 200, and press refrigerant sufficient in reclaiming, then power saves the impact that can make up clearance and bring, thus promotes the COP of rotary compressor 100.
As shown in Figure 7, along with S
1/ V
1change from small to big, the COP of rotary compressor 100 be first large from little change, to steadily, again to the process declined, as can be seen from Figure 7, work as S
1/ V
1ratio at 0.6 ‰ (mm
-1) ~ 1.2 ‰ (mm
-1) between time, adopt the COP of the rotary compressor 100 of the injection channel of this set on cylinder 22 higher.
As shown in Figure 8, when this rotary compressor 100 is applied in heat pump 200, along with S
1/ V
1change from small to big, the refrigerating capacity of rotary compressor 100 be also first large from little change, to steadily, again to the process declined, as can be seen from Figure 8, work as S
1/ V
1ratio at 0.6 ‰ (mm
-1) ~ 1.2 ‰ (mm
-1) between time, the refrigerating capacity of heat pump 200 is also higher.
With reference to Fig. 3 composition graphs 4, the head (i.e. one end of contiguous compression chamber 221) spraying valve seat 225 is formed with circular receiving cavity 227, circular receiving cavity 227 can be formed by the corresponding end-faces of cylinder 22 is recessed towards the other end of cylinder 22, jetburner 226 is formed on the inwall of circular receiving cavity 227, and jetburner 226 can be formed as round-shaped and coaxially arrange with circular receiving cavity 227.
Wherein, the radius of circular receiving cavity 227 is R
1(mm), the shape of cross section of compression chamber 221 is circular, and the radius of compression chamber 221 is R
2(mm), the distance between the center of circular receiving cavity 227 and the center of compression chamber 221 is L (mm), R
1, R
2, L meet: L=R
1+ R
2+ (0.2 ~ 0.7) mm.Thus, by being set between circular receiving cavity 227 and compression chamber 221 certain distance that is spaced apart from each other, this distance can for any number (comprising endpoint value) in 0.2mm ~ 0.7mm, can prevent the inner circle wall of the compression chamber 221 when both distances are the too near edge crossing with communicating passage 228 from easily coming off on the one hand, especially under cryogenic conditions, when the difference of spraying the whiff pressure of refrigerant and the pressure of inspiration(Pi) of cylinder 22 is larger, come off very risky, thus affect the reliability of rotary compressor 100, the situation causing rotary compressor 100 hydraulic performance decline when this distance is greater than 0.7mm can be prevented on the other hand.
As shown in Figure 5, the degree of depth of communicating passage 228 is h
1, the degree of depth of circular receiving cavity 227 is h
2, wherein h
1, h
2meet: h
2=h
1+ (0.1 ~ 0.5) mm.That is, between the inwall of circular receiving cavity 227 and the inwall of communicating passage 228, there is certain height difference, this height difference can for any number (comprising endpoint value) in 0.1mm ~ 0.5mm, and the degree of depth of communicating passage 228 is less than the degree of depth of circular receiving cavity 227, thus, the work efficiency of spraying valve seat 225 can be significantly improved, such as 30%, and, this height difference can ensure the injection flow spraying refrigerant, thus improve refrigeration and/or the heating capacity of rotary compressor 100, and then improve the performance of rotary compressor 100.
With reference to Fig. 2 and Fig. 4, the Extreme breadth of communicating passage 228 is d
1, the Extreme breadth of cylinder exhaust port 223 is d
2, wherein, d
1/ d
2meet: 0.4≤d
1/ d
2≤ 1.2.When rotary compressor 100 is applied in heat pump 200, as shown in figure 11, work as d
1/ d
2ratio between 0.4 ~ 1.2 time, the refrigerating capacity of rotary compressor 100 and power are all roughly higher.Further, d
1/ d
2meet further: 0.8≤d
1/ d
2≤ 1.0.Thus, the injection flow spraying refrigerant can be ensured, thus improve refrigeration and/or the heating capacity of rotary compressor 100, and then improve the performance of rotary compressor 100, and the reflation speed of clearance volume can be reduced, reduce the power of rotary compressor 100.
According to another embodiment of the present utility model, as shown in figure 12, injection channel is formed at least one in main bearing 21 and supplementary bearing 23, now injection channel can only be formed on main bearing 21, also only can be formed on supplementary bearing 23, or can also be formed on main bearing 21 and supplementary bearing 23 simultaneously.A side end face of the contiguous cylinder 22 of at least one in main bearing 21 and supplementary bearing 23 is run through in one end of injection channel, and wherein injection valve is piston 24.
In the process that piston 24 rolls along the inner circle wall of compression chamber 221, the corresponding end-faces of piston 24 can above-mentioned one end of shutoff injection channel in section sometime, injection refrigerant now in injection channel can not enter in compression chamber 221, and the corresponding end-faces of piston 24 can avoid above-mentioned one end of injection channel in another time period, the injection refrigerant now in injection channel can be entered in compression chamber 221 by above-mentioned one end of injection channel.
Alternatively, S
1/ V
1meet: 0.08 ‰ (mm
-1)≤S
1/ V
1≤ 0.6 ‰ (mm
-1).Thus, adopt the rotary compressor 100 of the injection channel of this set on main bearing 21 and/or supplementary bearing 23, improve the efficiency of this rotary compressor 100.
According to further embodiment of the present utility model, with reference to Fig. 1 and in conjunction with Figure 13 and Figure 14, rotary compressor 100 comprises further: jet liquid-storage container 3, and jet liquid-storage container 3 is located at outside housing 1, and jet liquid-storage container 3 is connected to pass into injection refrigerant in injection channel with injection channel.Thus, by arranging jet liquid-storage container 3, can the injection refrigerant flowing through jet liquid-storage container 3 be separated further, produce liquid hit phenomenon to prevent liquid refrigerants from entering in compression chamber 221.
Specifically, jet liquid-storage container 3 comprises: shell 31 and go out pipe 32, shell 31 is formed with import 311 and outlet, such as, as shown in figure 13, import 311 is formed in the top of shell 31, spraying refrigerant can enter in shell 31 by import 311, outlet is formed in the bottom of shell 31, go out one end of pipe 32 (such as, upper end in Figure 13) stretch in shell 31 through outlet, and the above-mentioned one end going out pipe 32 extend into the top in shell 31, the above-mentioned one end going out pipe 32 is closed, and the sidewall going out above-mentioned one end of pipe 32 is formed with at least one side direction vent 321, side direction vent 321 runs through pipe 32 along the thickness direction going out pipe 32, wherein go out the other end of pipe 32 (such as, lower end in Figure 13) be communicated with injection channel, for the injection refrigerant flowing through out pipe 32 is delivered to injection channel.Thus, by arranging side direction vent 321, can prevent liquid coolant from entering in compression chamber 221 further, extending the working life of the parts such as housing 1 inner compressor structure.
Cylinder assembly comprises an above-mentioned cylinder 22, at this moment, rotary compressor 100 can be single cylinder compressor or multicylinder compressor, when rotary compressor 100 is multicylinder compressor, now sprays refrigerant and only passes in the compression chamber 221 of one of them in multiple cylinder 22.Effective liquid storage volume of jet liquid-storage container 3 is V
2, now V
2/ V
1meet: 1.5≤V
2/ V
1≤ 4.Wherein, V
1for the swept volume of the cylinder 22 in single cylinder compressor, or one of them the swept volume of cylinder 22 above-mentioned in multiple cylinders 22 of multicylinder compressor.
When rotary compressor 100 is applied in heat pump 200, carry out gas-liquid separation saturated vapor out through flash vessel 203 and spray refrigerant exactly, but in some operating mode especially varying load process, flash vessel 203 stream condition is chaotic, spray refrigerant and can contain liquid refrigerants, by by V
2/ V
1be set to satisfied 1.5≤V
2/ V
1≤ 4, now jet liquid-storage container 3 is less, reduce the heat-exchange performance of jet liquid-storage container 3 and surrounding, heat exchange amount reduces, make to spray the temperature of refrigerant and can remain on a lower temperature, thus obvious to the cold service of compression chamber 221, and spray the reduction of refrigerant specific volume, improve the COP of rotary compressor 100.
Reference Fig. 9 also in conjunction with Figure 10, works as V
2/ V
1ratio between 1.5 ~ 4 time, the COP of rotary compressor 100 is higher.Further, V
2/ V
1meet further: 1.9≤V
2/ V
1≤ 2.8.Here, it should be noted that, " effective liquid storage volume of jet liquid-storage container 3 " can be understood as side direction vent less than 321, shell 31 and goes out the volume of the liquid that can store between pipe 32.
Cylinder assembly comprises multiple above-mentioned cylinder 22, and at this moment, rotary compressor 100 is multicylinder compressor, now sprays refrigerant and passes in the compression chamber 221 of at least two in multiple cylinder 22.Effective liquid storage volume of jet liquid-storage container 3 is V
2, the swept volume sum of multiple cylinder 22 is V
1', wherein V
2/ V
1' meet: 1.2≤V
2/ V
1'≤3.Wherein, V
1' be the swept volume of the cylinder 22 of above-mentioned at least two in multiple cylinders 22 of multicylinder compressor.Further, V
2/ V
1' meet further: 1.5≤V
2/ V
1'≤2.2.
With reference to Figure 13 and Figure 14, side direction vent 321 is multiple, and multiple side direction vent 321 is symmetrical along the circumference going out pipe 32.Thus, by arranging multiple side direction vent 321, not only can ensure injection flow, preventing liquid refrigerants from entering in compression chamber 221 further, and by being arranged symmetrically with, the gas flow rate spraying refrigerant can being stablized, reduce jet flow resistance loss, improve efficiency.Alternatively, the number of side direction vent 321 is 4 ~ 10.Be appreciated that side direction vent 321 number and go out arrangement on pipe 32 etc. can according to actual requirement adaptive change, the utility model does not do concrete restriction to this.
Alternatively, the area sum of at least one side direction vent 321 is S2, and wherein S2/S1 meets: 1≤S2/S1≤4.Go out pipe 32 for pipe, and the smallest cross-section area going out pipe 32 is S3, wherein S2/S3 meets: 0.5≤S2/S3≤1.3.Wherein, when side direction vent 321 is one, S2 is the area of this side direction vent 321; When side direction vent 321 is multiple, S2 is the area of this multiple side direction vent 321.Thus, minimum injection circulation area can be ensured, thus ensure to meet the requirement of injection flow, and flow velocity when can stablize injection and fluidised form, reduce jet flow resistance loss, improve efficiency.
As shown in figure 14, jet liquid-storage container 3 also comprises: net-filter assembly 33, and net-filter assembly 33 is located in shell 31, and net-filter assembly 33 is positioned at above-mentioned one end of pipe 32.Thus, by arranging net-filter assembly 33, can prevent impurity from entering in compression chamber 221, and the refrigerant fluidised form in jet liquid-storage container 3 can be stablized further, thus liquid refrigerants not easily enters in compression chamber 221.
Further, with reference to Fig. 1 and Figure 15, rotary compressor 100 also comprises: air-breathing liquid-storage container 4, and air-breathing liquid-storage container 4 is located at outside housing 1, and air-breathing liquid-storage container 4 is communicated with to feed refrigerant to be compressed in compression chamber 221 with the cylinder intakeport 224 of cylinder 22.Thus, by arranging air-breathing liquid-storage container 4, can prevent liquid refrigerants from entering in compression chamber 221 and producing liquid hit phenomenon.
According to the rotary compressor 100 of the utility model embodiment, rotary compressor 100 rational in infrastructure, reliable operation, ability are suitable, efficiency is high, vibrating noise is low, and long service life.
As shown in figure 15, according to the heat pump 200 of the utility model second aspect embodiment, comprising: according to rotary compressor 100, two heat exchangers 201, two throttling arrangements 202 and the flash vessel 203 of the above-mentioned first aspect embodiment of the utility model.Wherein, heat pump 200 has heat-production functions.
One end of one of them in two heat exchangers 201 (such as, left end in Figure 15) be connected with the intakeport 41 of rotary compressor 100, intakeport 41 for passing into refrigerant to be compressed in rotary compressor 100, another one end in two heat exchangers 201 (such as, left end in Figure 15) be connected with the relief opening 11 of rotary compressor 100, relief opening 11 is for discharging the refrigerant after compression from the housing 1 of rotary compressor 100.Wherein, two heat exchangers 201 can be respectively vaporizer and condenser.
Two throttling arrangements 202 are located between the other end (right-hand member such as, in Figure 15) of two heat exchangers 201.Alternatively, throttling arrangement 202 is capillary tube or electric expansion valve etc.Flash vessel 203 is located between two throttling arrangements 202, and wherein flash vessel 203 is communicated with to pass into injection refrigerant in injection channel with injection channel.
Further, heat pump 200 also comprises four-way valve 204, with reference to Figure 15, four-way valve 204 comprises the first valve port, the second valve port, the 3rd valve port and the 4th valve port, first valve port is connected with one of them the above-mentioned one end above-mentioned in two heat exchangers 201, second valve port is connected with relief opening 11, and the 3rd valve port is connected with intakeport 41, and the 4th valve port is connected with another the above-mentioned one end above-mentioned in two heat exchangers 201.When the cooling and heating circulatory system is run in cooling mode, the first valve port of four-way valve 204 and the second valve port conducting, the 3rd valve port and the 4th valve port conducting; When the cooling and heating circulatory system is run in a heating mode, the first valve port of four-way valve 204 and the 3rd valve port conducting, the second valve port and the 4th valve port conducting.
According to the heat pump 200 of the utility model embodiment, improve the overall performance of heat pump 200.
According to the air-conditioning system of the utility model third aspect embodiment, comprising: according to rotary compressor 100, two heat exchangers 201, two throttling arrangements 202 and the flash vessel 203 of the above-mentioned first aspect embodiment of the utility model.Wherein, air-conditioning system only can have refrigerating function, also can have refrigeration and heat-production functions simultaneously.
One end of one of them in two heat exchangers 201 is connected with the intakeport 41 of rotary compressor 100, another one end in two heat exchangers 201 is connected with the relief opening 11 of rotary compressor 100, two throttling arrangements 202 are located between the other end of two heat exchangers 201, flash vessel 203 is located between two throttling arrangements 202, and wherein flash vessel 203 is communicated with to pass into injection refrigerant in injection channel with injection channel.Here, it should be noted that, be all described in detail in the description on the application such as the concrete structure of heat exchanger 201, throttling arrangement 202 and flash vessel 203 etc., do not repeat them here.
According to the air-conditioning system of the utility model embodiment, improve the overall performance of air-conditioning system.
To form according to other of the rotary compressor 100 of the utility model embodiment, heat pump 200 and air-conditioning system and operation is all known to those skilled in the art, be not described in detail here.
In the description of this specification, specific features, structure, material or feature that the description of reference term " embodiment ", " some embodiments ", " illustrative examples ", " example ", " concrete example " or " some examples " etc. means to describe in conjunction with this embodiment or example are contained at least one embodiment of the present utility model or example.In this manual, identical embodiment or example are not necessarily referred to the schematic representation of above-mentioned term.And the specific features of description, structure, material or feature can combine in an appropriate manner in any one or more embodiment or example.
Although illustrate and described embodiment of the present utility model, those having ordinary skill in the art will appreciate that: can carry out multiple change, amendment, replacement and modification to these embodiments when not departing from principle of the present utility model and aim, scope of the present utility model is by claim and equivalents thereof.
Claims (22)
1. a rotary compressor, is characterized in that, comprising:
Housing;
Compressing mechanism, described compressing mechanism comprises main bearing, cylinder assembly, supplementary bearing and piston, described main bearing and described supplementary bearing are located at the axial two ends of described cylinder assembly respectively, described cylinder assembly comprises cylinder, described cylinder has compression chamber, described piston is located in described compression chamber and inwall along described compression chamber can roll, described cylinder is formed with cylinder exhaust port, described compressing mechanism is formed with injection channel, described injection channel is used for passing into injection refrigerant in described compression chamber, the pressure of described injection refrigerant is greater than the pressure of inspiration(Pi) of described cylinder, and be less than the exhaust pressure of described cylinder, the smallest cross-section area of wherein said injection channel is S
1mm
2, the swept volume of described cylinder is V
1mm
3, described S
1/ V
1meet: 0.08 ‰ mm
-1≤ S
1/ V
1≤ 1.2 ‰ mm
-1, and
Injection valve, described injection valve is located on described compressing mechanism to control conducting and the partition of described injection channel and described compression chamber.
2. rotary compressor according to claim 1, is characterized in that, described injection channel comprises:
Spray valve seat, described injection valve seat is formed on the end face of described cylinder, and the inwall of described injection valve seat is formed with jetburner, and described injection refrigerant passes in described compression chamber by described jetburner,
Wherein said injection valve is located to open and close described jetburner on described injection valve seat, and described injection valve is configured to open described jetburner when the pressure in described compression chamber is less than the pressure at described jetburner place, cut out described jetburner when the pressure in described compression chamber is greater than the pressure at described jetburner place; With
Communicating passage, described communicating passage is located between described injection valve seat and described compression chamber to be communicated with described injection valve seat and described compression chamber.
3. rotary compressor according to claim 2, is characterized in that, described S
1/ V
1meet: 0.6 ‰ mm
-1≤ S
1/ V
1≤ 1.2 ‰ mm
-1.
4. rotary compressor according to claim 2, is characterized in that, the head of described injection valve seat is formed with circular receiving cavity, and described jetburner is formed on the inwall of described circular receiving cavity,
The radius of wherein said circular receiving cavity is R
1mm, the radius of described compression chamber is R
2mm, the distance between the center of described circular receiving cavity and the center of described compression chamber is Lmm, wherein said R
1, R
2, L meet:
L＝R
1+R
2+(0.2～0.7)mm。
5. rotary compressor according to claim 4, is characterized in that, the degree of depth of described communicating passage is h
1, the degree of depth of described circular receiving cavity is h
2, wherein said h
1, h
2meet: h
2=h
1+ (0.1 ~ 0.5) mm.
6. rotary compressor according to claim 2, is characterized in that, the Extreme breadth of described communicating passage is d
1, the Extreme breadth of described cylinder exhaust port is d
2, wherein d
1/ d
2meet: 0.4≤d
1/ d
2≤ 1.2.
7. rotary compressor according to claim 6, is characterized in that, described d
1/ d
2meet further: 0.8≤d
1/ d
2≤ 1.0.
8. rotary compressor according to claim 1, it is characterized in that, described injection channel is formed at least one in described main bearing and described supplementary bearing, at least one the side end face of the described cylinder of vicinity described in described main bearing and described supplementary bearing is run through in one end of described injection channel, and wherein said injection valve is described piston.
9. rotary compressor according to claim 8, is characterized in that, described S
1/ V
1meet: 0.08 ‰ mm
-1≤ S
1/ V
1≤ 0.6 ‰ mm
-1.
10. the rotary compressor according to any one of claim 1-9, is characterized in that, comprises further:
Jet liquid-storage container, described jet liquid-storage container is located at outside described housing, and described jet liquid-storage container is connected to pass into described injection refrigerant in described injection channel with described injection channel.
11. rotary compressors according to claim 10, is characterized in that, described cylinder assembly comprises a described cylinder, and effective liquid storage volume of described jet liquid-storage container is V
2, wherein said V
2/ V
1meet: 1.5≤V
2/ V
1≤ 4.
12. rotary compressors according to claim 11, is characterized in that, described V
2/ V
1meet further: 1.9≤V
2/ V
1≤ 2.8.
13. rotary compressors according to claim 10, is characterized in that, described cylinder assembly comprises multiple described cylinder, and effective liquid storage volume of described jet liquid-storage container is V
2, the swept volume sum of described multiple cylinder is V
1', wherein said V
2/ V
1' meet: 1.2≤V
2/ V
1'≤3.
14. rotary compressors according to claim 13, is characterized in that, described V
2/ V
1' meet further: 1.5≤V
2/ V
1'≤2.2.
15. rotary compressors according to claim 10, is characterized in that, described jet liquid-storage container comprises:
Shell, described shell is formed with import and outlet; With
Go out pipe, described go out one end of pipe stretch in described shell through described outlet, described go out described one end of pipe close, and described in go out described one end of pipe sidewall on be formed with at least one side direction vent, wherein said go out the other end of pipe be communicated with described injection channel.
16. rotary compressors according to claim 15, is characterized in that, described side direction vent for multiple and described multiple side direction vent along described in go out the circumference of pipe symmetrical.
17. rotary compressors according to claim 16, is characterized in that, the number of described side direction vent is 4 ~ 10.
18. rotary compressors according to claim 15, is characterized in that, the area sum of at least one side direction vent described is S
2, wherein said S
2/ S
1meet: 1≤S
2/ S
1≤ 4.
19. rotary compressors according to claim 15, is characterized in that, the area sum of at least one side direction vent described is S
2, described in go out pipe for pipe, and described in go out pipe smallest cross-section area be S
3, wherein said S
2/ S
3meet: 0.5≤S
2/ S
3≤ 1.3.
20. rotary compressors according to claim 15, is characterized in that, described jet liquid-storage container also comprises:
Net-filter assembly, described net-filter assembly to be located in described shell and to go out described one end of pipe described in being positioned at.
21. 1 kinds of heat pumps, is characterized in that, comprising:
Rotary compressor according to any one of claim 1-20;
Two heat exchangers, the one end of one of them in described two heat exchangers is connected with the intakeport of described rotary compressor, and another the one end in described two heat exchangers is connected with the relief opening of described rotary compressor;
Two throttling arrangements, described two throttling arrangements are located between the other end of described two heat exchangers; And
Flash vessel, described flash vessel is located between described two throttling arrangements, and wherein said flash vessel is communicated with to pass into described injection refrigerant in described injection channel with described injection channel.
22. 1 kinds of air-conditioning systems, is characterized in that, comprising:
Rotary compressor according to any one of claim 1-20;
Two heat exchangers, the one end of one of them in described two heat exchangers is connected with the intakeport of described rotary compressor, and another the one end in described two heat exchangers is connected with the relief opening of described rotary compressor;
Two throttling arrangements, described two throttling arrangements are located between the other end of described two heat exchangers; And
Flash vessel, described flash vessel is located between described two throttling arrangements, and wherein said flash vessel is communicated with to pass into described injection refrigerant in described injection channel with described injection channel.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520232718.3U CN204755311U (en) | 2015-04-16 | 2015-04-16 | Rotary compressor and heat pump system , air conditioning system that have it |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520232718.3U CN204755311U (en) | 2015-04-16 | 2015-04-16 | Rotary compressor and heat pump system , air conditioning system that have it |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN204755311U true CN204755311U (en) | 2015-11-11 |
Family
ID=54470023
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201520232718.3U Withdrawn - After Issue CN204755311U (en) | 2015-04-16 | 2015-04-16 | Rotary compressor and heat pump system , air conditioning system that have it |
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| Country | Link |
|---|---|
| CN (1) | CN204755311U (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104791251A (en) * | 2015-04-16 | 2015-07-22 | 广东美芝制冷设备有限公司 | Rotary compressor, heat pump system employing rotary compressor and air-conditioning system employing rotary compressor |
| CN105864047A (en) * | 2016-05-30 | 2016-08-17 | 安徽美芝精密制造有限公司 | Rotary compressor shell assembly, rotary compressor and refrigerating system |
| CN110594154A (en) * | 2019-09-06 | 2019-12-20 | 珠海凌达压缩机有限公司 | Compressor, air conditioner refrigerating system and air conditioner |
| CN113530822A (en) * | 2021-08-27 | 2021-10-22 | 广东美芝精密制造有限公司 | Rotary compressor and air conditioning equipment |
-
2015
- 2015-04-16 CN CN201520232718.3U patent/CN204755311U/en not_active Withdrawn - After Issue
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104791251A (en) * | 2015-04-16 | 2015-07-22 | 广东美芝制冷设备有限公司 | Rotary compressor, heat pump system employing rotary compressor and air-conditioning system employing rotary compressor |
| CN105864047A (en) * | 2016-05-30 | 2016-08-17 | 安徽美芝精密制造有限公司 | Rotary compressor shell assembly, rotary compressor and refrigerating system |
| CN105864047B (en) * | 2016-05-30 | 2019-06-07 | 安徽美芝精密制造有限公司 | Rotary compressor casing assembly, rotary compressor and refrigeration system |
| CN110594154A (en) * | 2019-09-06 | 2019-12-20 | 珠海凌达压缩机有限公司 | Compressor, air conditioner refrigerating system and air conditioner |
| CN113530822A (en) * | 2021-08-27 | 2021-10-22 | 广东美芝精密制造有限公司 | Rotary compressor and air conditioning equipment |
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|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20151111 Effective date of abandoning: 20180717 |
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| AV01 | Patent right actively abandoned |
Granted publication date: 20151111 Effective date of abandoning: 20180717 |