CN108087238B - Compressor and air conditioning system with same - Google Patents
Compressor and air conditioning system with same Download PDFInfo
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- CN108087238B CN108087238B CN201711071346.0A CN201711071346A CN108087238B CN 108087238 B CN108087238 B CN 108087238B CN 201711071346 A CN201711071346 A CN 201711071346A CN 108087238 B CN108087238 B CN 108087238B
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- compression cylinder
- stage compression
- compressor
- air
- evaporator
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- 238000004378 air conditioning Methods 0.000 title claims abstract description 25
- 230000006835 compression Effects 0.000 claims abstract description 75
- 238000007906 compression Methods 0.000 claims abstract description 75
- 239000003507 refrigerant Substances 0.000 claims abstract description 28
- 238000004891 communication Methods 0.000 claims description 4
- 238000005336 cracking Methods 0.000 claims 3
- 238000005057 refrigeration Methods 0.000 abstract description 6
- 239000007788 liquid Substances 0.000 description 9
- 230000000694 effects Effects 0.000 description 7
- 238000010586 diagram Methods 0.000 description 6
- 230000001502 supplementing effect Effects 0.000 description 6
- 238000000034 method Methods 0.000 description 5
- 230000007423 decrease Effects 0.000 description 3
- 238000001816 cooling Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000014509 gene expression Effects 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 238000004781 supercooling Methods 0.000 description 1
- 239000013589 supplement Substances 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
- F04B39/122—Cylinder block
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/07—Details of compressors or related parts
- F25B2400/074—Details of compressors or related parts with multiple cylinders
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The invention provides a compressor and an air conditioning system with the same, wherein the compressor comprises a shell, a pump body assembly and an enthalpy increasing component, and the pump body assembly comprises: the first-stage compression cylinder and the second-stage compression cylinder are both arranged in the shell; the middle cavity is arranged in the shell, the refrigerant flowing out of the first-stage compression cylinder enters the second-stage compression cylinder after passing through the middle cavity, and the middle cavity is provided with a make-up air flow inlet communicated with the enthalpy increasing component; wherein, the working volume V1 of the first stage compression cylinder and the working volume V2 of the second stage compression cylinder satisfy the following relationship: the value range of V2/V1 is 0.56-0.75. The technical scheme of the invention effectively solves the problems that the air conditioner in the prior art has serious refrigeration capacity attenuation at high outdoor temperature, is difficult to meet the indoor refrigeration capacity requirement and has poor comfortableness.
Description
Technical Field
The invention relates to the field of air conditioners, in particular to a compressor and an air conditioning system with the same.
Background
As the outdoor ambient temperature increases, the indoor cooling capacity demand increases, but the air conditioning cooling capacity decreases as the outdoor temperature increases. This is due to the fact that an increase in ambient temperature increases the air condensing temperature, which in turn leads to an increase in compressor discharge pressure, an increase in compressor operating pressure differential, a decrease in volumetric efficiency, and a decrease in refrigerant circulation flow. As the superheat degree of the exhaust is increased and the supercooling temperature of the liquid is increased, the enthalpy difference of the refrigerant at the inlet and outlet of the evaporator is reduced, and the refrigerating capacity of the air conditioner is further reduced.
In tropical and desert areas (such as middle east areas), the outdoor environment temperature can reach more than 50 ℃ at most, the refrigerating capacity attenuation of an air conditioner is serious, and indoor refrigerating requirements are difficult to meet; on the other hand, because the exhaust pressure is higher, the compressor operates under the working condition of high pressure difference and high exhaust temperature for a long time, the operation load of the compressor is large, the abrasion is faster, and the service life is shorter.
Disclosure of Invention
The invention aims to provide a compressor and an air conditioning system with the compressor, so as to solve the problems that in the prior art, the air conditioner is serious in refrigeration capacity attenuation at high outdoor temperature, and is difficult to meet indoor refrigeration capacity requirements, and the comfort is poor.
In order to achieve the above object, according to one aspect of the present invention, there is provided a compressor including a housing, a pump body assembly, and an enthalpy increasing member, the pump body assembly including: the first-stage compression cylinder and the second-stage compression cylinder are both arranged in the shell; the middle cavity is arranged in the shell, the refrigerant flowing out of the first-stage compression cylinder enters the second-stage compression cylinder after passing through the middle cavity, and the middle cavity is provided with a make-up air flow inlet communicated with the enthalpy increasing component; wherein, the working volume V1 of the first stage compression cylinder and the working volume V2 of the second stage compression cylinder satisfy the following relationship: the value range of V2/V1 is 0.56-0.75.
Further, the working volume V1 of the first stage compression cylinder and the working volume V2 of the second stage compression cylinder further satisfy the following relationship: the value range of V2/V1 is 0.64-0.68.
Further, the ratio of the equivalent diameter Dm of the make-up air inlet to the equivalent diameter D1 of the air inlet of the first stage compression cylinder is lambda, and lambda takes a value in the range of 0.3-0.7.
Further, the air supplementing valve plate and the valve plate baffle are arranged at the air supplementing inlet.
Further, the intermediate chamber also has an intake port in communication with the intake port of the first stage compression cylinder and an exhaust port in communication with the intake port of the second stage compression cylinder.
Further, the second stage compression cylinder is located the top of first stage compression cylinder, and the below of first stage compression cylinder is provided with flange structure, and the intermediate chamber forms in flange structure.
According to another aspect of the present invention, there is provided an air conditioning system including a compressor, the compressor being the compressor described above.
Further, the air conditioning system further comprises an evaporator, a condenser and a flash evaporator, wherein the evaporator is connected with an air inlet of the compressor, the condenser is connected with an air outlet of the compressor, an inlet of the flash evaporator is connected with the condenser, a first outlet of the flash evaporator is connected with the evaporator, a second outlet of the flash evaporator is connected with an enthalpy increasing part of the compressor, and a pressure relief valve is arranged between the second outlet of the flash evaporator and the enthalpy increasing part.
Further, the pressure relief valve has a opening pressure P1, the opening pressure P1 is larger than the inlet pressure Ps of the compressor and smaller than the outlet pressure Pd of the compressor, and the opening pressure P1 has a value range of
Further, the value range of the opening pressure P1 is
Further, a first throttling device is arranged between the condenser and the flash evaporator, and/or a second throttling device is arranged between the flash evaporator and the evaporator.
By applying the technical scheme of the invention, the compressor is provided with the enthalpy increasing component and the middle cavity, and the middle cavity is provided with the air supplementing inlet communicated with the enthalpy increasing component. Therefore, the compressor of the present embodiment may start the air-supplementing enthalpy-increasing after the outdoor temperature reaches the predetermined value. When the air charge and the enthalpy are increased, the refrigerant flowing into the intermediate chamber from the enthalpy increasing component through the air charge inlet is mixed with the refrigerant flowing out of the first-stage compression cylinder and then is sucked into the second-stage compression cylinder. The refrigerating capacity is obviously higher than that of a refrigerating system adopting a conventional compressor through the process, and the refrigerating capacity and the comfort of the air conditioning system at high temperature are improved. Meanwhile, the ratio V2/V1 of the working volume V1 of the first-stage compression cylinder to the working volume V2 of the second-stage compression cylinder is selected to be 0.56-0.75, and the performance of the compressor in the non-air-supplementing mode and the air-supplementing mode can be simultaneously satisfied.
Drawings
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention. In the drawings:
FIG. 1 shows a schematic cross-sectional view of an embodiment of a compressor according to the present invention;
FIG. 2 shows an enlarged view at A of the compressor of FIG. 1;
FIG. 3 shows a schematic structural view of an intermediate chamber of the compressor of FIG. 1;
fig. 4 shows a schematic cross-sectional view of an embodiment of an air conditioner according to the present invention;
FIG. 5 is a schematic diagram showing an air conditioning system employing the compressor of FIG. 1 in comparison with the operation effect of a conventional compression system;
FIG. 6 is a schematic diagram showing the working volume ratio of the compressor of FIG. 1 versus performance impact in two modes of operation; and
FIG. 7 is a schematic diagram showing the effect of make-up gas inlet parameters on compressor performance for the compressor of FIG. 1.
Wherein the above figures include the following reference numerals:
10. a housing; 20. a first stage compression cylinder; 30. a second stage compression cylinder; 40. an intermediate chamber; 41. a make-up gas inlet; 42. a gas supplementing valve plate; 43. a valve plate baffle; 44. an air suction port; 45. an exhaust port; 50. a flange structure; 61. an evaporator; 62. a condenser; 63. a flash evaporator; 64. a pressure relief valve; 65. a first throttle device; 66. a second throttle device; 70. an enthalpy increasing member; 100. a compressor.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. The following description of at least one exemplary embodiment is merely exemplary in nature and is in no way intended to limit the invention, its application, or uses. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of example embodiments in accordance with the present application. As used herein, the singular is also intended to include the plural unless the context clearly indicates otherwise, and furthermore, it is to be understood that the terms "comprises" and/or "comprising" when used in this specification are taken to specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof.
The relative arrangement of the components and steps, numerical expressions and numerical values set forth in these embodiments do not limit the scope of the present invention unless it is specifically stated otherwise. Meanwhile, it should be understood that the sizes of the respective parts shown in the drawings are not drawn in actual scale for convenience of description. Techniques, methods, and apparatus known to one of ordinary skill in the relevant art may not be discussed in detail, but should be considered part of the specification where appropriate. In all examples shown and discussed herein, any specific values should be construed as merely illustrative, and not a limitation. Thus, other examples of the exemplary embodiments may have different values. It should be noted that: like reference numerals and letters denote like items in the following figures, and thus once an item is defined in one figure, no further discussion thereof is necessary in subsequent figures.
Aiming at the problems in the background art, the invention provides a two-stage enthalpy-increasing rotary compressor, which is particularly suitable for air conditioners in middle east regions, can solve the problem of outdoor high Wen Shikong modulation cold attenuation, can improve the reliability of the compressor, and realizes long-term reliable operation of the rotary compressor in high-temperature regions.
As shown in fig. 1 to 3, the compressor of the present embodiment includes a housing 10, a pump body assembly, and an enthalpy increasing member 70, the pump body assembly including: first stage compression cylinder 20, second stage compression cylinder 30, and intermediate chamber 40. The first stage compression cylinder 20 and the second stage compression cylinder 30 are both disposed within the housing 10. The intermediate chamber 40 is provided in the casing 10, and the refrigerant flowing out of the first-stage compression cylinder 20 passes through the intermediate chamber 40 and then enters the second-stage compression cylinder 30, and the intermediate chamber 40 has a make-up air inlet 41 communicating with the enthalpy increasing member 70. Wherein the working volume V1 of the first stage compression cylinder 20 and the working volume V2 of the second stage compression cylinder 30 satisfy the following relationship:
the value range of V2/V1 is 0.56-0.75.
With the technical solution of the present embodiment, the compressor is provided with an enthalpy increasing member 70 and an intermediate chamber 40, the intermediate chamber 40 having a make-up air flow inlet 41 communicating with the enthalpy increasing member 70. Therefore, the compressor of the present embodiment may start the air-supplementing enthalpy-increasing after the outdoor temperature reaches the predetermined value. At the time of supplementing the gas and increasing the enthalpy, the refrigerant flowing from the enthalpy adding part 70 into the intermediate chamber through the supplementing gas inlet 41 is mixed with the refrigerant flowing out of the first-stage compression cylinder 20 and then sucked into the second-stage compression cylinder 30. The refrigerating capacity is obviously higher than that of a refrigerating system adopting a conventional compressor through the process, and the refrigerating capacity and the comfort of the air conditioning system at high temperature are improved. Meanwhile, in the embodiment, the ratio V2/V1 of the working volume V1 of the first-stage compression cylinder 20 to the working volume V2 of the second-stage compression cylinder 30 is selected to be 0.56-0.75, so that the performance of the compressor in the non-air-supplementing mode and the air-supplementing mode can be simultaneously satisfied.
Fig. 5 is a schematic diagram showing an air conditioning system to which the compressor of fig. 1 is applied in comparison with the operation effect of a conventional compression system. The dotted line in the figure represents the operation effect of the conventional stand-alone compression system, and the solid line in the figure represents the operation effect of the air conditioning system to which the compressor of fig. 1 is applied. As can be seen from fig. 5, the air conditioning system using the compressor of the embodiment is in the air-supplementing off state when the outdoor temperature does not reach T043 ℃, and is opened to supplement air and increase enthalpy when the outdoor temperature reaches T043 ℃, the refrigerating capacity is significantly higher than that of a refrigerating system using a conventional compressor, and the refrigerating capacity and the comfort of the air conditioner at high temperature are improved.
Fig. 6 shows a schematic diagram of the working volume ratio of the compressor of fig. 1 versus performance in two modes of operation. The upper curve in the figure is the performance curve in the on-air-make-up mode, and the lower curve in the figure is the performance curve in the off-air-make-up mode. In the air-supplementing mode, the volume ratio is too large or too small, so that the balance of the compression ratio of the two-stage air cylinders is influenced, and the overall efficiency is influenced; when the air supply is started, the volume ratio is too large, the compression power increased by the increase of the air supply amount is too large, the COP energy efficiency ratio is reduced, the volume ratio is too small, the refrigerating capacity lifting amount caused by the air supply is too small, and the COP energy efficiency ratio is also reduced. As can be seen from the figures: in this embodiment, the ratio V2/V1 of the working volume V1 of the first stage compression cylinder 20 to the working volume V2 of the second stage compression cylinder 30 is selected to be 0.56-0.75, so that the performance of the compressor in both modes can be simultaneously satisfied. The compressor of the embodiment can not only improve the refrigerating efficiency of the compressor under the condition of air supply, but also realize the optimal energy efficiency under the condition of air supply.
Further preferably, the working volume V1 of the first stage compression cylinder 20 and the working volume V2 of the second stage compression cylinder 30 further satisfy the following relationship: the value range of V2/V1 is 0.64-0.68. The compressor performance is at this point optimal.
As shown in fig. 2, in the present embodiment, the ratio of the equivalent diameter Dm of the make-up air inlet 41 to the equivalent diameter D1 of the intake port of the first-stage compression cylinder 20 is λ, which takes a value in the range of 0.3 to 0.7. The compressor performance is now better. This is because if λ is too small, the flow resistance of the make-up air increases rapidly, while λ is too large and the flow of the make-up air is too slow, the heat loss of the make-up air is too large, affecting the quality of the make-up air. FIG. 7 is a schematic diagram showing the effect of make-up gas inlet parameters on compressor performance for the compressor of FIG. 1. As can also be seen from the graph, the compressor performance is better when the lambda value ranges from 0.3 to 0.7.
As shown in fig. 3, in the present embodiment, a valve plate 42 and a valve plate baffle 43 are disposed at the air make-up inlet 41. The air make-up valve 42 and the valve plate shutter 43 determine the open condition of the air make-up inlet 41, and the air make-up inlet 41 is opened when the refrigerant pressure at the air make-up inlet 41 is greater than a predetermined value.
As shown in fig. 3, in the present embodiment, the intermediate chamber 40 further has an intake port 44 communicating with the intake port of the first-stage compression cylinder 20 and an exhaust port 45 communicating with the intake port of the second-stage compression cylinder 30. A valve plate is also provided at the suction port 44. The suction port 44, the exhaust port 45 and the make-up air inlet 41 are all provided on the outer wall of the intermediate chamber and on the same plane.
As shown in fig. 1, the second stage compression cylinder 30 is located above the first stage compression cylinder 20, a flange structure 50 is provided below the first stage compression cylinder 20, and the intermediate chamber 40 is formed in the flange structure 50. The flange structure 50 is a lower flange, and the lower flange is concave inward to form the middle chamber 40.
The first stage compression cylinder 20 is further provided with a flow passage communicating the intake port of the second stage compression cylinder 30 and the exhaust port 45 of the intermediate chamber 40, and a flow passage communicating the enthalpy increasing member 70 and the make-up air inlet 41.
The compressor of this embodiment further includes a knockout, a motor, a crankshaft, a flange, a cover plate, a partition plate, and refrigerating fluid, and these structures are substantially the same as those in the prior art, and are not described herein again.
The invention also provides an air conditioning system, as shown in fig. 4, the air conditioning system according to the invention comprises a compressor, and the compressor is the compressor. By adopting the compressor, the refrigerating capacity and the comfort of the air conditioning system at high temperature are improved. Meanwhile, the performance of the compressor in the non-air-supplementing mode and the air-supplementing mode can be simultaneously satisfied.
As shown in fig. 4, in the present embodiment, the air conditioning system further includes an evaporator 61, a condenser 62, and a flash evaporator 63, the evaporator 61 is connected to an air inlet of the compressor 100, the condenser 62 is connected to an air outlet of the compressor 100, an inlet of the flash evaporator 63 is connected to the condenser 62, a first outlet (gas outlet) of the flash evaporator 63 is connected to the evaporator 61, a second outlet of the flash evaporator 63 is connected to an enthalpy increasing part 70 of the compressor, and a pressure relief valve 64 is provided between the second outlet (liquid outlet) of the flash evaporator 63 and the enthalpy increasing part 70. The air conditioning system of the present embodiment may be automatically switched to supply air according to the operating pressure through the pressure relief valve 64.
The relief valve 64 has an opening pressure P1, and when the operating pressure is greater than P1, the relief valve 64 opens; when the operating pressure is less than P1, the relief valve 64 closes. The opening pressure P1 is larger than the air inlet pressure Ps of the compressor and smaller than the air outlet pressure Pd of the compressor, and the value range of the opening pressure P1 isThe energy efficiency of the compressor operation is optimal when the opening pressure P1 satisfies the above conditions.
Further preferably, the opening pressure P1 has a value in the range of
As shown in fig. 4, a first throttle device 65 is provided between the condenser 62 and the flash evaporator 63, and a second throttle device 66 is provided between the flash evaporator 63 and the evaporator 61.
Referring to fig. 1 and 4, the refrigerant flowing process of the air conditioning system of the present embodiment is as follows:
the compressor 100 sucks low-temperature and low-pressure refrigerant flowing out of the evaporator 61 (see reference numeral 1 in fig. 1), compresses the refrigerant by the first-stage compression cylinder 20, discharges the refrigerant to the intermediate chamber 40 (see reference numeral 2 in fig. 1), the second-stage compression cylinder 30 sucks the refrigerant from the intermediate chamber 40, discharges the compressed refrigerant to high temperature and high pressure, discharges the refrigerant to the pump body (see reference numeral 5 in fig. 1), discharges the refrigerant through the compressor discharge pipe (see reference numeral 6 in fig. 1) after flowing through the motor, releases heat by the condenser 62 to form high-pressure liquid refrigerant, changes the high-pressure liquid refrigerant into medium-pressure refrigerant of gas-liquid two phases by the first throttling device 65, separates the gas from the liquid by the flash evaporator 63, flows into the intermediate chamber (see reference numeral 3 in fig. 1) by the pressure relief valve 64, and the first-stage compression cylinder 20 discharges the gas, mixes the compressed refrigerant, and then sucks the medium-pressure refrigerant into the second-stage compression cylinder (see reference numeral 4 in fig. 1), throttles the medium-stage refrigerant by the second throttling device 66, and absorbs the heat and changes the high-pressure liquid refrigerant into low-pressure liquid refrigerant to the liquid refrigerant by the separator of the compressor 100.
From the above description, it can be seen that the above embodiments of the present invention achieve the following technical effects:
1. the invention provides a double-stage enthalpy-increasing rotary compressor and an air conditioner circulating system, which can ensure higher energy efficiency of an air conditioner under a conventional refrigeration working condition, can realize the improvement of refrigeration output under a high-temperature environment, and particularly has the remarkable advantages of energy conservation and comfort in middle east and other climatic hot areas;
2. the invention provides a switching device for controlling the switch air supply of a two-stage enthalpy-increasing compressor, which can automatically switch the switch air supply according to the outdoor temperature and has the characteristics of low cost and reliable switching;
3. the invention discloses a double-stage enthalpy-increasing rotary compressor, which provides an optimal volume ratio (ratio of working volume of a high-pressure stage cylinder to working volume of a low-pressure stage cylinder) range, can improve the indication efficiency of the compressor under the condition of air supply, and also realizes optimal energy efficiency under the condition of air supply.
In the description of the present invention, it should be understood that the azimuth or positional relationships indicated by the azimuth terms such as "front, rear, upper, lower, left, right", "lateral, vertical, horizontal", and "top, bottom", etc., are generally based on the azimuth or positional relationships shown in the drawings, merely to facilitate description of the present invention and simplify the description, and these azimuth terms do not indicate and imply that the apparatus or elements referred to must have a specific azimuth or be constructed and operated in a specific azimuth, and thus should not be construed as limiting the scope of protection of the present invention; the orientation word "inner and outer" refers to inner and outer relative to the contour of the respective component itself.
Spatially relative terms, such as "above … …," "above … …," "upper surface at … …," "above," and the like, may be used herein for ease of description to describe one device or feature's spatial location relative to another device or feature as illustrated in the figures. It will be understood that the spatially relative terms are intended to encompass different orientations in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, elements described as "above" or "over" other devices or structures would then be oriented "below" or "beneath" the other devices or structures. Thus, the exemplary term "above … …" may include both orientations of "above … …" and "below … …". The device may also be positioned in other different ways (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.
In addition, the terms "first", "second", etc. are used to define the components, and are only for convenience of distinguishing the corresponding components, and the terms have no special meaning unless otherwise stated, and therefore should not be construed as limiting the scope of the present invention.
The above description is only of the preferred embodiments of the present invention and is not intended to limit the present invention, but various modifications and variations can be made to the present invention by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (10)
1. Compressor, characterized in that, including casing (10), pump body subassembly and increase enthalpy part (70), pump body subassembly includes:
a first-stage compression cylinder (20) and a second-stage compression cylinder (30), both the first-stage compression cylinder (20) and the second-stage compression cylinder (30) being disposed within the housing (10);
an intermediate chamber (40) provided in the casing (10), wherein the refrigerant flowing out of the first-stage compression cylinder (20) passes through the intermediate chamber (40) and then enters the second-stage compression cylinder (30), and the intermediate chamber (40) is provided with a make-up air inlet (41) communicated with the enthalpy increasing component (70);
wherein the working volume V1 of the first stage compression cylinder (20) and the working volume V2 of the second stage compression cylinder (30) satisfy the following relationship:
the value range of V2/V1 is 0.56-0.75;
the ratio of the equivalent diameter Dm of the make-up air inlet (41) to the equivalent diameter D1 of the air inlet of the first-stage compression cylinder (20) is lambda, and lambda takes a value in the range of 0.3-0.7.
2. Compressor according to claim 1, characterized in that the working volume V1 of the first stage compression cylinder (20) and the working volume V2 of the second stage compression cylinder (30) further satisfy the following relationship:
the value range of V2/V1 is 0.64-0.68.
3. Compressor according to claim 1, characterized in that the make-up air inlet (41) is provided with a make-up air valve (42) and a valve flap (43).
4. The compressor of claim 1, wherein the intermediate chamber (40) further has an intake port (44) in communication with the exhaust port of the first stage compression cylinder (20) and an exhaust port (45) in communication with the intake port of the second stage compression cylinder (30).
5. Compressor according to claim 1, characterized in that the second stage compression cylinder (30) is located above the first stage compression cylinder (20), a flange structure (50) being provided below the first stage compression cylinder (20), the intermediate chamber (40) being formed in the flange structure (50).
6. An air conditioning system comprising a compressor, wherein the compressor is the compressor of any one of claims 1 to 5.
7. The air conditioning system according to claim 6, further comprising an evaporator (61), a condenser (62) and a flash evaporator (63), the evaporator (61) being connected to an air inlet of the compressor, the condenser (62) being connected to an air outlet of the compressor, an inlet of the flash evaporator (63) being connected to the condenser (62), a first outlet of the flash evaporator (63) being connected to the evaporator (61), a second outlet of the flash evaporator (63) being connected to an enthalpy increasing part (70) of the compressor, a pressure relief valve (64) being provided between the second outlet of the flash evaporator (63) and the enthalpy increasing part (70).
8. The air conditioning system according to claim 7, wherein the pressure relief valve (64) has a cracking pressure P1, the cracking pressure P1 being greater than an intake pressure Ps of the compressor and less than an exhaust pressure Pd of the compressor, the cracking pressure P1 being in a range of values
9. The air conditioning system according to claim 8, wherein the opening pressure P1 has a value in a range of
10. An air conditioning system according to claim 7, characterized in that a first throttling device (65) is arranged between the condenser (62) and the flash evaporator (63), and/or a second throttling device (66) is arranged between the flash evaporator (63) and the evaporator (61).
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711071346.0A CN108087238B (en) | 2017-11-03 | 2017-11-03 | Compressor and air conditioning system with same |
| PCT/CN2018/091619 WO2019085501A1 (en) | 2017-11-03 | 2018-06-15 | Compressor and an air-conditioning system having same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711071346.0A CN108087238B (en) | 2017-11-03 | 2017-11-03 | Compressor and air conditioning system with same |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108087238A CN108087238A (en) | 2018-05-29 |
| CN108087238B true CN108087238B (en) | 2024-04-02 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201711071346.0A Active CN108087238B (en) | 2017-11-03 | 2017-11-03 | Compressor and air conditioning system with same |
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| WO (1) | WO2019085501A1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN108087238B (en) * | 2017-11-03 | 2024-04-02 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and air conditioning system with same |
| CN110242577A (en) * | 2019-05-06 | 2019-09-17 | 珠海凌达压缩机有限公司 | Compressor and air conditioner |
| CN110206733A (en) * | 2019-07-09 | 2019-09-06 | 珠海格力节能环保制冷技术研究中心有限公司 | Double-stage compression multi-air-supply compressor and air conditioner |
| CN110617645B (en) * | 2019-10-23 | 2024-09-03 | 珠海凌达压缩机有限公司 | Carbon dioxide compressor and refrigerating system thereof |
| CN118517415B (en) * | 2024-07-22 | 2024-09-27 | 珠海凌达压缩机有限公司 | Valve plate, pump body assembly, enthalpy-increasing compressor and air conditioner |
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Also Published As
| Publication number | Publication date |
|---|---|
| CN108087238A (en) | 2018-05-29 |
| WO2019085501A1 (en) | 2019-05-09 |
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