CN106762648B - Compressor, refrigerating system and car - Google Patents
Compressor, refrigerating system and car Download PDFInfo
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- CN106762648B CN106762648B CN201710062725.7A CN201710062725A CN106762648B CN 106762648 B CN106762648 B CN 106762648B CN 201710062725 A CN201710062725 A CN 201710062725A CN 106762648 B CN106762648 B CN 106762648B
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- compressor
- piston
- compression
- compression cavity
- cylinder
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/02—Pumps characterised by combination with or adaptation to specific driving engines or motors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/80—Other components
Abstract
The invention discloses a compressor, a refrigeration system and an automobile, wherein the compressor adopts CO2The refrigerant just includes: a housing; compression mechanism ofThe compression mechanism is arranged in the shell and comprises at least one cylinder, the cylinder is provided with a compression cavity with a circular cross section, a sliding sheet groove communicated with the compression cavity is arranged on the cylinder, a piston which can roll along the peripheral wall of the compression cavity and is eccentrically arranged relative to the compression cavity is arranged in the compression cavity, and a sliding sheet which can move along the sliding sheet groove and is stopped on the piston is arranged in the sliding sheet groove; the motor is arranged in the shell and is in transmission connection with the piston, wherein the piston has an eccentricity e relative to the compression cavity, the length of the slide sheet is L, the thickness of the slide sheet is T, and L.T/e is not less than 17.1 and not more than 23.9. The compressor according to the embodiment of the invention adopts CO2The refrigerant has the advantages of small abrasion, reasonable stress range, high reliability and the like.
Description
Technical Field
The invention relates to the technical field of compressors, in particular to a compressor, a refrigeration system with the compressor and an automobile with the refrigeration system.
Background
For the compressor, various size parameters of a compression mechanism of the compressor have a crucial influence on various performances of the compressor, and in order to achieve ideal performance, interaction schemes for various parameters of the compressor are proposed in the related art, for example, an interaction scheme for a cylinder height and a cylinder inner diameter, an interaction scheme for a cylinder inner diameter and a piston outer diameter, and an interaction scheme for a slide sheet thickness and a cylinder inner diameter, but the interaction schemes are all directed to the compressor adopting refrigerants such as R410A, R22 and R134a, and are applied to the compressor adopting CO, and the compressor adopting refrigerants such as R410A, R22 and R134a2For the compressor of refrigerant, CO is used2The above-mentioned alternative is not suitable for CO because the working pressure of the refrigerant is significantly higher than the working pressure of the refrigerants such as R410A, R22, R134a2The refrigerant compressor, and the above-mentioned interaction scheme is based on the interaction of two parameters, can't satisfy and adopt CO2The performance of the compressor of the refrigerant is improved.
Disclosure of Invention
The present invention is directed to solving, at least to some extent, one of the above-mentioned problems in the related art. To this end, the invention proposes a compressor using CO2The refrigerant has the advantages of small abrasion, reasonable stress range, high reliability and the like.
The invention also provides a refrigerating system with the compressor.
The invention also provides an automobile with the refrigerating system.
To achieve the above object, an embodiment according to a first aspect of the present invention proposes a compressor that employs CO2The refrigerant just includes: a housing; the compression mechanism is arranged in the shell and comprises at least one cylinder, the cylinder is provided with a compression cavity with a circular cross section, a sliding sheet groove communicated with the compression cavity is arranged on the cylinder, a piston which can roll along the peripheral wall of the compression cavity and is eccentrically arranged relative to the compression cavity is arranged in the compression cavity, and a sliding sheet which can move along the sliding sheet groove and is stopped against the piston is arranged in the sliding sheet groove; the motor is arranged in the shell and is in transmission connection with the piston, wherein the piston has an eccentricity e relative to the compression cavity, the length of the slide sheet is L, the thickness of the slide sheet is T, and L.T/e is not less than 17.1 and not more than 23.9.
The compressor according to the embodiment of the invention adopts CO2The refrigerant has the advantages of small abrasion, reasonable stress range, high reliability and the like.
In addition, the compressor according to the embodiment of the present invention may further have the following additional technical features:
according to one embodiment of the invention, 1.8mm ≦ e.
According to one embodiment of the invention e.ltoreq.3.6 mm.
According to one embodiment of the invention, 1.8 mm. ltoreq. e.ltoreq.3.6 mm.
According to one embodiment of the invention, the CO is2The working pressure of the refrigerant is 3.5MPa to 14.5 MPa.
According to one embodiment of the invention, the housing has an internal cavity with a circular cross-section, the diameter of the internal cavity being Dca, 80mm Dca 120 mm.
According to an embodiment of the present invention, a compression spring is disposed in the slide groove, and the slide normally abuts against the outer circumferential surface of the piston under an elastic force of the compression spring.
According to an embodiment of the present invention, the compressor further comprises: the liquid storage device is arranged outside the shell, and the compression cavity is provided with an air suction port communicated with the liquid storage device.
Embodiments according to the second aspect of the invention propose a refrigeration system comprising a compressor according to embodiments of the first aspect of the invention.
The refrigeration system according to the embodiment of the invention has the advantages of high reliability and the like by utilizing the compressor according to the embodiment of the invention.
Embodiments according to a third aspect of the invention propose a motor vehicle comprising a refrigeration system according to embodiments of the second aspect of the invention.
According to the automobile provided by the embodiment of the invention, the refrigerating system provided by the embodiment of the invention has the advantages of reliable performance and the like.
Drawings
Fig. 1 is a schematic structural view of a compressor according to an embodiment of the present invention.
Fig. 2 is a schematic structural view of a compression mechanism of a compressor according to an embodiment of the present invention.
Fig. 3 is a vane slot and vane structure diagram of a compressor according to an embodiment of the present invention.
Fig. 4 is a rear view illustrating a vane groove of a compressor according to an embodiment of the present invention.
FIG. 5 is a force diagram of a vane of the compressor according to an embodiment of the present invention.
FIG. 6 is a graph of vane slot wear versus endurance time for a compressor according to an embodiment of the present invention.
FIG. 7 is a graph of sectional stress at the tail of a vane slot versus length, thickness and eccentricity of a piston for a compressor in accordance with an embodiment of the present invention.
Fig. 8 is a graph of energy efficiency ratio versus piston eccentricity for a compressor according to an embodiment of the present invention.
Reference numerals:
a compressor 1,
The air compressor comprises a shell 10, an air cylinder 20, a compression cavity 21, a slide sheet groove 22, a section 23, a piston 30, a slide sheet 40, a compression spring 50, a liquid storage device 60 and a motor 70.
Detailed Description
Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are illustrative and intended to be illustrative of the invention and are not to be construed as limiting the invention.
In the related art, two dimensional parameter interaction schemes are proposed for compressors using refrigerants such as R410A, R22, R134a, and the like, for example, in order to improve the energy efficiency ratio, the ratio of the cylinder height to the cylinder inner diameter is not more than 0.4, the ratio of the cylinder inner diameter to the piston outer diameter is not less than 0.452 and not more than 0.520, the ratio of the vane thickness to the cylinder inner diameter is not less than 0.041 and not more than 0.067, and the ratio of the vane length to the piston eccentricity is not less than 0.165 and not more than 0.225.
And for the use of CO2Compressor of refrigerant due to CO2The working pressure of the refrigerant is far greater than that of the refrigerants such as R410A, R22 and R134a, so the proposal is not suitable for or partially not suitable for adopting CO2The refrigerant compressor adopts the technical scheme that the energy efficiency ratio is improved, the reliability is hardly improved, and CO is adopted for the compressor with higher working pressure2The reliability of the refrigerant compressor is just a prominent problem.
In view of the state of the compressor in the related art, the present invention proposes a compressor adapted to use CO2The compressor of refrigerant and technical scheme that can improve reliability.
A compressor 1 according to an embodiment of the present invention is described below with reference to the accompanying drawings.
As shown in fig. 1 to 8, the compressor 1 according to the embodiment of the present invention employs CO2The refrigerant includes a housing 10, a compression mechanism, and a motor 70.
The compression mechanism is provided in the housing 10 and includes at least one cylinder 20. The cylinder 20 is provided with a compression chamber 21 with a circular cross section, a sliding sheet groove 22 communicated with the compression chamber 21 is arranged on the cylinder 20, a piston 30 which can roll along the peripheral wall of the compression chamber 21 and is eccentrically arranged relative to the compression chamber 21 is arranged in the compression chamber 21, and a sliding sheet 40 which can move along the sliding sheet groove 22 and is stopped against the piston 30 is arranged in the sliding sheet groove 22. The motor 70 is disposed in the housing 10 and is in transmission connection with the piston 30 for driving the piston 30 to roll.
Wherein, the eccentricity of the piston 30 relative to the compression chamber 21 is e, the length of the slide sheet 40 is L, the thickness of the slide sheet 40 is T, L.T/e is more than or equal to 17.1 and less than or equal to 23.9.
As shown in FIG. 3, the thickness of the slide groove 22 is T ', T' is approximately equal to (1.004-1.008). T in order to form a lubricating oil film, namely, a certain gap is formed between the slide 40 and the slide groove 22. When the compressor 1 is operated, as shown in fig. 5, the suction side pressure Ps of the vane 40 is smaller than the discharge side pressure Pd, the vanes 40 are inclined by the differential pressure, and the inclination angle of the vane 40 with respect to the vane groove 22 is θ, and it can be understood that when T/T' is fixed, the smaller L/e is, the larger θ is, the worse the stress state of the vane 40 is, and the larger the wear of the vane groove 22 is. Meanwhile, the smaller the thickness T of the vane 40, the greater the amount of deformation of the vane 40 and the greater the wear of the vane 40. For the use of CO2The above problem is more prominent in the refrigerant compressor 1 because the value of Pd — Ps is much larger than that of the refrigerant using R410A, R22, R134a, and the like. The ranges of L, e, and T are necessarily optimized, and the compressor 1 according to the embodiment of the present invention can reduce wear and control the stress range by designing an interactive scheme of three dimensional parameters of L, e, and T, thereby achieving the effect of improving the reliability of the compressor.
The following describes in detail the design process of the interactive scheme of the three dimensional parameters L, e, and T of the compressor 1 according to the embodiment of the present invention, and tests show that the technical effect of the interactive scheme is achieved.
In general, wear of a sliding pair of a compressor is an important index for measuring reliability of the sliding pair of the compressor. The applicant found that the wear amount of the slide sheet 40 has a certain correlation with L · T/e, and fig. 6 is a graph showing the results of the endurance test, in which the abscissa is the endurance time T, the ordinate is the wear Δ of the slide groove 22, and the dotted line indicates the allowable wear value. It can be seen that the smaller L.T/e, the greater the wear of the vane groove 22 at the same durability time. When L · T/e is 15.5, 15.9, and 16.5, the wear of the vane groove 22 tends to increase continuously when the durability time reaches 2500 hours, that is, the wear is still progressive. When L · T/e is 17.1, the wear of the vane groove 22 does not increase, that is, the wear does not progress, when the durability time reaches about 1000 hours. Therefore, when L.T/e is not less than 17.1, the wear of the slide groove 22 can be controlled within the allowable range.
Further, the length L of the slide 40 is also limited by the structural dimensions. Specifically, as shown in FIGS. 2-5, the wall thickness m at the tail of the vane slot 22 of the cylinder 20 is related to the length L of the vane 40 and the thickness T of the vane 40. When the inner diameter Dca of the cylinder 20 and the diameter Dcy of the compression chamber 21 are constant, the length L of the sliding piece 40 should not be too long, and the thickness T of the sliding piece 40 should not be too thick, otherwise the wall thickness m at the tail of the sliding piece groove 22 of the cylinder 20 would be too small, and the stress of the section 23 would exceed the allowable stress range of the cylinder material, causing the reliability problem of the cylinder 20. For CO2In the refrigerant compressor, the pressure difference between the inside and the outside of the cylinder 20 is large, which is a more serious problem. Applicants have found that the maximum stress at the aft end of the vane slot 22 of the cylinder 20 is also related to L.T/e, and FIG. 7 shows the change in cross-sectional stress σ at the aft end of the vane slot 22 as Dca and Dcy remain unchanged and as L.T/e increases, with the dashed lines indicating the desired stress values, and it can be seen that when L.T/e is increased>At 23.9, the stress sigma of the tail section of the slide plate groove 22 exceeds the allowable stress of the material, so that when the L.T/e is less than or equal to 23.9, the stress sigma of the tail section of the slide plate groove 22 can be ensured to be in the allowable stress range of the material.
Therefore, the compressor 1 according to the embodiment of the present invention employs CO2The refrigerant has the advantages of small abrasion, reasonable stress range, high reliability and the like.
It should be understood by those skilled in the art that the compression mechanism of the compressor 1 according to the embodiment of the present invention may include more than one cylinder, such as two cylinders, three cylinders, four cylinders, etc., wherein any one of the cylinders may satisfy the above-mentioned size parameters, and preferably, all the cylinders satisfy the above-mentioned size parameters.
A compressor 1 according to an embodiment of the present invention is described below with reference to the accompanying drawings.
As shown in fig. 1 to 8, the compressor 1 according to the embodiment of the present invention employs CO2The refrigerant includes a housing 10, a compression mechanism, and a motor 70.
Specifically, as shown in fig. 1, a compression spring 50 is disposed in the vane slot 22, and the vane 40 is normally abutted against the outer circumferential surface of the piston 30 under the elastic force of the compression spring 50, so as to ensure the sealing property between the vane 40 and the piston 30 and not to affect the eccentric rolling of the piston 30.
Further, as shown in fig. 1, the compressor 1 further includes an accumulator 60, the accumulator 60 is disposed outside the casing 10, the compression cavity 21 has a suction port communicated with the accumulator 60, and the accumulator 60 stores low-pressure refrigerant and performs gas-liquid separation, filtration, and the like.
In some embodiments of the present invention, the eccentricity e of the piston 30 with respect to the compression chamber 21 is 1.8mm or more, i.e., 1.8 mm. ltoreq.e, in order to improve volumetric efficiency to improve the energy efficiency ratio, and the eccentricity e of the piston 30 with respect to the compression chamber 21 is 3.6mm or less, i.e., e.ltoreq.3.6 mm, in order to reduce friction loss.
Preferably, 1.8 mm. ltoreq. e.ltoreq.3.6 mm. Therefore, the energy efficiency ratio can be improved, the friction loss can be controlled, namely, the energy efficiency ratio and the reliability of the compressor 1 are considered at the same time, the relation between the energy efficiency ratio and the eccentric amount e is shown in fig. 8, and it can be seen that the energy efficiency ratio of the compressor is optimal when e is 1.8-3.6 mm.
In some specific examples of the invention, the CO is2The working pressure of the refrigerant is 3.5-14.5 MPa, which is much higher than the working pressure of the refrigerants such as R410A, R22, R134a, etc., and the inner diameter Dca of the shell 10 is not suitable to be designed to be too large, because Dca is larger, the wall thickness of the shell 10 is designed to be thicker to meet the working pressure requirement of the CO2 refrigerant, and the compressor 1 is heavier. The size of the compressor 1, Dca according to the embodiment of the invention is designed to be 80-120mm, namely Dca is more than or equal to 80mm and less than or equal to 120mm, so that the requirement of CO can be met2The working volume of the refrigerant can control the wall thickness of the shell 10, thereby ensuring the volume and weight of the compressor 1.
A refrigeration system according to an embodiment of the present invention is described below with reference to the accompanying drawings. The refrigeration system according to the embodiment of the present invention includes the compressor 1 according to the above-described embodiment of the present invention.
The refrigeration system according to the embodiment of the present invention has the advantages of high reliability and the like by using the compressor 1 according to the above-described embodiment of the present invention.
An automobile according to an embodiment of the present invention is described below with reference to the drawings. The automobile according to the embodiment of the invention comprises the refrigeration system according to the above embodiment of the invention.
According to the automobile provided by the embodiment of the invention, the refrigerating system provided by the embodiment of the invention has the advantages of reliable performance and the like.
Other constructions and operations of refrigeration systems and automobiles according to embodiments of the present invention are known to those of ordinary skill in the art and will not be described in detail herein.
In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", and the like, indicate orientations and positional relationships based on those shown in the drawings, and are used only for convenience of description and simplicity of description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be considered as limiting the present invention.
Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means at least two, e.g., two, three, etc., unless specifically limited otherwise.
In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples described in this specification can be combined and combined by those skilled in the art.
Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention, and that variations, modifications, substitutions and alterations can be made to the above embodiments by those of ordinary skill in the art within the scope of the present invention.
Claims (7)
1. A compressor, characterized in that the compressor uses CO2The refrigerant just includes:
a housing;
the compression mechanism is arranged in the shell and comprises at least one cylinder, the cylinder is provided with a compression cavity with a circular cross section, a sliding sheet groove communicated with the compression cavity is arranged on the cylinder, a piston which can roll along the peripheral wall of the compression cavity and is eccentrically arranged relative to the compression cavity is arranged in the compression cavity, and a sliding sheet which can move along the sliding sheet groove and is stopped against the piston is arranged in the sliding sheet groove;
a motor arranged in the shell and connected with the piston in a transmission way,
wherein the eccentricity of the piston relative to the compression cavity is e, the length of the slide sheet is L, the thickness of the slide sheet is T, L.T/e is more than or equal to 17.1 and less than or equal to 23.9,
1.8mm≤e≤3.6mm。
2. the compressor of claim 1, wherein the CO is2The working pressure of the refrigerant is 3.5MPa to 14.5 MPa.
3. The compressor of claim 1, wherein the housing has an internal cavity with a circular cross-section, the internal cavity having a diameter Dca, 80mm Dca 120 mm.
4. The compressor according to any one of claims 1 to 3, wherein a compression spring is provided in the vane groove, and the vane is stopped against the outer circumferential surface of the piston by an elastic force of the compression spring.
5. The compressor of any one of claims 1-3, further comprising:
the liquid storage device is arranged outside the shell, and the compression cavity is provided with an air suction port communicated with the liquid storage device.
6. Refrigeration system, characterized in that it comprises a compressor according to any one of claims 1-5.
7. An automobile, characterized by comprising a refrigeration system according to claim 6.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201710062725.7A CN106762648B (en) | 2017-01-24 | 2017-01-24 | Compressor, refrigerating system and car |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201710062725.7A CN106762648B (en) | 2017-01-24 | 2017-01-24 | Compressor, refrigerating system and car |
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| CN106762648A CN106762648A (en) | 2017-05-31 |
| CN106762648B true CN106762648B (en) | 2020-11-24 |
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Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6432657B1 (en) | 2017-08-24 | 2018-12-05 | 株式会社富士通ゼネラル | Rotary compressor |
| CN110863987B (en) * | 2019-11-29 | 2021-08-27 | 安徽美芝精密制造有限公司 | Compressor and refrigeration equipment |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3723458B2 (en) * | 2001-02-14 | 2005-12-07 | 三洋電機株式会社 | Rotary compressor |
| JP4008471B2 (en) * | 2003-01-20 | 2007-11-14 | 松下電器産業株式会社 | Rotary compressor |
| JP2010025103A (en) * | 2008-06-16 | 2010-02-04 | Daikin Ind Ltd | Rotary compressor |
| CN102094169A (en) * | 2009-12-09 | 2011-06-15 | 台州市百达制冷有限公司 | Surface PVD coating method for blade (slip sheet) for novel compressor |
| CN202833169U (en) * | 2012-07-24 | 2013-03-27 | 广东美芝制冷设备有限公司 | Rotating compressor |
| JP6091303B2 (en) * | 2013-04-12 | 2017-03-08 | 三菱電機株式会社 | Rolling piston compressor |
| CN205860542U (en) * | 2016-07-28 | 2017-01-04 | 广东美芝制冷设备有限公司 | Carbon dioxide refrigerating system |
| CN206429399U (en) * | 2017-01-24 | 2017-08-22 | 广东美芝制冷设备有限公司 | Compressor, refrigeration system and automobile |
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