CN110821831B

CN110821831B - Single-cylinder compressor and heat exchange working equipment

Info

Publication number: CN110821831B
Application number: CN201911281325.0A
Authority: CN
Inventors: 曹小军; 周杏标; 江波; 吴延平; 程鹏
Original assignee: Anhui Meizhi Precision Manufacturing Co Ltd
Current assignee: Anhui Meizhi Precision Manufacturing Co Ltd
Priority date: 2019-12-11
Filing date: 2019-12-11
Publication date: 2021-06-25
Anticipated expiration: 2039-12-11
Also published as: CN110821831A

Abstract

The application belongs to the technical field of compressors and relates to a single-cylinder compressor and heat exchange working equipment. In the single-cylinder compressor, when the single-cylinder compressor works, the driving motor drives the crankshaft to rotate, the piston arranged outside the eccentric part of the crankshaft moves in the cylinder, the slip sheet is elastically and slidably arranged in the chute of the cylinder, and the head of the slip sheet is abutted to the outer peripheral surface of the piston, so that a refrigerant is compressed and discharged. The ratio of the product of the height of the cylinder and the inner diameter of the cylinder to the inner diameter of the shell is set to be 15.5-16.5 mm, the ratio of the two times of the eccentric amount of the crankshaft to the inner diameter of the cylinder is set to be 0.2-0.23, the pump body structure with small shell inner diameter and large displacement can be realized, and over-compression loss and leakage are improved. The ratio of the sum of the eccentric amount and the length of the slip sheet to the inner radius of the cylinder is set to be 1.13-1.17, the ratio of the product of the radius of the head of the slip sheet and the thickness of the slip sheet to the length of the slip sheet is set to be 0.74-0.8 mm, the problem of the sound of the slip sheet of the compressor under the working condition of low frequency and low pressure difference can be effectively solved, and the power consumption can be reduced. The service performance of the heat exchange working equipment is ensured.

Description

Single-cylinder compressor and heat exchange working equipment

Technical Field

The application belongs to the technical field of compressors and relates to a single-cylinder compressor and heat exchange working equipment.

Background

Under the era background that the problems of resource environment constraint and global climate change are increasingly serious, low carbon, energy conservation and emission reduction are the development trends and targets of the industry. Under the premise of improving the technology and ensuring the performance of heat exchange working equipment, various enterprises strive to reduce material consumption and cost, and make the whole machine be miniaturized and light-weighted, for example, when a compressor is applied to an air conditioner, the outdoor unit needs to be miniaturized. For a double-cylinder compressor, the gas compression torque has an overlapping area on a phase angle, so that lower noise vibration can be generated, but more space of the compressor is occupied. With the rapid development of the electric control torque compensation technology of the motor, the vibration of the single-cylinder compressor at a low frequency range can be well controlled. Compared with a double-cylinder compressor, the single-cylinder compressor has one less piston and one less sliding vane, the mechanical efficiency of the pump body is higher, the occupied space is reduced, the design of miniaturization and light weight is easy to realize, and the discharge capacity is relatively smaller. There is a need in the industry for a compressor with a compact structure, and the sliding vane can reliably slide in the sliding slot of the cylinder, so as to reduce the flying rate of the sliding vane.

Disclosure of Invention

An object of the embodiment of this application is to provide a single cylinder compressor to solve prior art and be difficult to provide a compact structure and the gleitbretter can be in the reliable gliding compressor's of cylinder spout technical problem.

The embodiment of the application provides a single cylinder compressor, includes:

a housing;

the driving motor is arranged in the shell; and

the compression mechanism comprises a main bearing arranged in the shell, an air cylinder arranged in the shell and provided with a sliding chute, a crankshaft which is provided with an eccentric part and is driven by the driving motor to rotate, an auxiliary bearing which supports the crankshaft together with the main bearing, a piston arranged in the air cylinder and sleeved outside the eccentric part, and a sliding sheet which is elastically and slidably arranged in the sliding chute, wherein the head part of the sliding sheet is abutted to the peripheral surface of the piston;

assuming that the height of the cylinder is Hcy, the inner diameter of the cylinder is Dcy, the inner diameter of the shell is Dy, the eccentric amount of the crankshaft is e, the length of the sliding piece is L, the thickness of the sliding piece is T, and the radius of the head of the sliding piece is r, the following relational expression is satisfied:

15.5mm≤Hcy×Dcy/Dy≤16.5mm；

0.2≤2e/Dcy≤0.23；

1.13≤2×(e+L)/Dcy≤1.17；

0.74mm≤r×T/L≤0.8mm。

optionally, the inner diameter of the housing is in the range of 100 to 110 mm.

Optionally, the height of the cylinder ranges from 30 to 36 mm; the inner diameter of the cylinder ranges from 46 to 48 mm; the eccentricity of the crankshaft ranges from 4 to 5.5 mm.

Optionally, the inner diameter of the housing is 101mm, the height of the cylinder is 36mm, the inner diameter of the cylinder is 46mm, and the eccentricity of the crankshaft is 5.2 mm;

or, the inner diameter of the housing is 101mm, the height of the cylinder is 32mm, the inner diameter of the cylinder is 46mm, and the eccentricity of the crankshaft is 4.6 mm.

Optionally, the ratio of the product of the height of the cylinder and the inner diameter of the cylinder to the inner diameter of the housing is 16.3 mm.

Optionally, the eccentricity of the crankshaft ranges from 4 to 5.5 mm.

Optionally, the length of the slip sheet ranges from 18.5 to 22.5 mm; the thickness of the slip sheet ranges from 2.8 to 4 mm; the radius of the head of the slide is in the range 3 to 6 mm.

Optionally, the length of the slider is 21.5 mm; the thickness of the slip sheet is 4 mm; the radius of the head of the slide is 4 mm.

Optionally, the head of the slide is provided with a hard film; or the whole surface of the sliding sheet is provided with a hard film.

Optionally, the cylinders have a displacement of 20 to 25 cc.

The embodiment of the application provides heat exchange working equipment which comprises the single-cylinder compressor.

One or more technical solutions provided in the embodiments of the present application have at least one of the following technical effects: in the single-cylinder compressor, when the single-cylinder compressor works, the driving motor drives the crankshaft to rotate, the piston arranged outside the eccentric part of the crankshaft moves in the cylinder, the slip sheet is elastically and slidably arranged in the chute of the cylinder, and the head of the slip sheet is abutted to the outer peripheral surface of the piston, so that a refrigerant is compressed and discharged. The ratio of the product of the height of the cylinder and the inner diameter of the cylinder to the inner diameter of the shell is set to be 15.5-16.5 mm, the ratio of the two times of the eccentric amount of the crankshaft to the inner diameter of the cylinder is set to be 0.2-0.23, the pump body structure with small shell inner diameter and large displacement can be realized, and over-compression loss and leakage are improved. The ratio of the sum of the eccentric amount and the length of the slip sheet to the inner radius of the cylinder is set to be 1.13-1.17, the ratio of the product of the radius of the head of the slip sheet and the thickness of the slip sheet to the length of the slip sheet is set to be 0.74-0.8 mm, the problem of the sound of the slip sheet of the compressor under the working condition of low frequency and low pressure difference can be effectively solved, the power consumption can be reduced, and the performance of normal use can be achieved. The heat exchange working equipment with the single-cylinder compressor has ensured use performance.

Drawings

In order to more clearly illustrate the technical solutions in the embodiments of the present application, the drawings needed to be used in the embodiments or the prior art descriptions will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present application, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without inventive exercise.

FIG. 1 is a cross-sectional view of a single cylinder compressor provided in an embodiment of the present application;

FIG. 2 is a perspective view of a cylinder employed in the single cylinder compressor of FIG. 1;

FIG. 3 is a schematic view of an assembly of a cylinder, a piston, a crankshaft and a vane for use in the single cylinder compressor of FIG. 1;

FIG. 4 is a schematic view of the assembly of the main bearings, the secondary bearings and the crankshaft used in the single cylinder compressor of FIG. 1;

FIG. 5 is a force analysis diagram of a vane of the single cylinder compressor provided in the embodiment of the present application at a low frequency of 9 Hz;

FIG. 6 is a graph of the resultant force experienced by the slider of FIG. 5 at a low frequency of 9 Hz;

FIG. 7 is a graph of 2 × (e + L)/Dcy vs. power consumption of the sliding vane side for a single cylinder compressor according to an embodiment of the present invention.

Detailed Description

In order to make the technical problems, technical solutions and advantageous effects to be solved by the present application clearer, the present application is further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the present application and are not intended to limit the present application.

In the description of the embodiments of the present application, it is to be understood that the terms "length," "width," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," and the like refer to orientations and positional relationships illustrated in the drawings, which are used for convenience in describing the embodiments of the present application and for simplicity in description, and do not indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and thus, are not to be construed as limiting the embodiments of the present application.

In the embodiments of the present application, unless otherwise specifically stated or limited, the terms "mounted," "connected," and "fixed" are to be construed broadly, e.g., as meaning 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 embodiments of the present application can be understood by those of ordinary skill in the art according to specific situations.

In order to meet the requirement of displacement, a single-cylinder compressor on the market is large in structure, for example, the inner diameter of a cylinder of the single-cylinder compressor is 120 mm. The double-cylinder compressor in the market is also bigger, for example, the cylinder internal diameter of a double-cylinder compressor is 110 mm. The existing single-cylinder compressor or double-cylinder compressor has the advantages that the overall structure occupies a large space, and accordingly, the structures of the driving motor and the compression mechanism are large, so that the manufacturing cost is high.

Referring to fig. 1 to 4, the embodiment of the present application provides a single-cylinder compressor, which can meet the requirements of large displacement and miniaturization, reduce the manufacturing cost, and improve the cost performance. The single cylinder compressor includes a casing 100, a driving motor 200, and a compression mechanism 300. The housing 100 is substantially cylindrical and is disposed in a vertical direction. The driving motor 200 and the compression mechanism 300 are vertically distributed in the casing 100 to form a vertical compressor. The driving motor 200 includes a stator 210 installed in the housing 100 and a rotor 220 coaxially installed in the stator 210, and the stator 210 generates a rotating magnetic field after being energized, and the rotor 220 rotates under the rotating magnetic field of the stator 210.

The compression mechanism 300 includes a main bearing 310 installed in the casing 100, a cylinder 320 installed in the casing 100, a crankshaft 330 having an eccentric portion 331 and rotated by the driving motor 200, a sub-bearing 340 supporting the crankshaft 330 together with the main bearing 310, a piston 350 installed in the cylinder 320 and sleeved outside the eccentric portion 331, and a vane 360 elastically slidably installed in the slide groove 322, and a head of the vane 360 is held in contact with an outer circumferential surface of the piston 350. A spring can be arranged in the sliding groove 322, so that the sliding sheet 360 is elastically installed in the sliding groove 322. The driving motor 200 rotates the crankshaft 330, and the crankshaft 330 is supported by the main bearings 310 and the sub bearings 340, so that the crankshaft 330 rotates smoothly. The piston 350 is disposed on the eccentric portion 331 of the crankshaft 330, the piston 350 is driven by the eccentric portion 331 to move, the slide piece 360 makes a reciprocating linear movement along the slide slot 322, and the slide piece 360 divides the inner cavity of the cylinder 320 into a high pressure cavity and a low pressure cavity with constantly changing volumes, thereby pressurizing the refrigerant.

The cylinder 320 is provided with a suction hole 321. The main bearing 310 is provided with an exhaust hole 311; alternatively, the main bearing 310 and the sub-bearing 340 are respectively provided with exhaust holes (311, 341). When the air compressor works, the driving motor 200 drives the crankshaft 330 to rotate, so that the piston 350 arranged outside the eccentric part 331 of the crankshaft 330 moves in the cylinder 320, further compresses the refrigerant entering from the air suction hole 321, and discharges the compressed refrigerant from the air discharge holes (311, 341).

Let the height of the cylinder be Hcy, the inner diameter of the cylinder be Dcy, the inner diameter of the housing be Dy, the eccentric amount of the crankshaft be e, which is the distance between the center line of the crankshaft 330 and the axis of the eccentric portion 331. The length of gleitbretter is L, and the thickness of gleitbretter is T, and the head radius of gleitbretter is r, satisfies following relational expression:

15.5mm≤Hcy×Dcy/Dy≤16.5mm； (1)

0.2≤2e/Dcy≤0.23； (2)

1.13≤2×(e+L)/Dcy≤1.17； (3)

0.74mm≤r×T/L≤0.8mm。 (4)

referring to fig. 3, for simplicity, the displacement is equal to the product of the cross-sectional area within the cylinder (excluding the area of the piston and crankshaft) and the height of the cylinder Hcy. When the cylinder inner diameter Dcy and the cylinder height Hcy are constant, the displacement increases as the cylinder inner cross-sectional area increases.

The internal cross-sectional area of the cylinder is S, the external diameter of the piston is Dh, and the following relational expression is satisfied:

S＝π*(Dcy²-Dh²)/4；

in the case where the cylinder inner diameter Dcy is constant, the larger the cylinder inner cross-sectional area S, the smaller the piston outer diameter Dh.

The eccentricity e satisfies the following relation:

e＝(Dcy-Dh)/2；

when the piston outer diameter Dh is decreased while the cylinder inner diameter Dcy is constant, the eccentric amount e is increased. That is, the eccentricity e increases, the piston outer diameter Dh decreases, and the displacement of the cylinder increases.

It is understood that the displacement is determined by three parameters, i.e., the cylinder bore Dcy, the cylinder height Hcy, and the eccentricity e. When designing the cylinder 320, the cylinder displacement is determined, and after the cylinder inner diameter Dcy, the cylinder height Hcy and the eccentricity e are determined, the piston outer diameter Dh is determined.

The compressor is required to realize small shell inner diameter Dy and large displacement. In the case of a small housing bore Dy, the cylinder bore Dcy cannot be too large, and the cylinder wall thickness must be thick to meet the strength requirements of the cylinder, so the size of the cylinder bore Dcy is limited by the structure of the cylinder itself. After the cylinder bore Dcy is determined, two ways of increasing the cylinder height Hcy and increasing the crankshaft eccentricity e can be adopted to realize large displacement.

Considering the relation (1), the molecular fraction Hcy × Dcy in Hcy × Dcy/Dy can be characterized as the volume of the cylinder 320 cavity, i.e., the displacement, when the crankshaft eccentricity e is determined. Dy is positively correlated with Dcy, and the larger Dy, the larger Dcy may be. Hcy × Dcy/Dy the larger this parameter is, the larger the displacement is, and the smaller the casing inner diameter Dy is. It was mentioned above that the cylinder height Hcy can be increased to achieve a large displacement. When Dcy is determined with Dy, Hcy becomes larger if Hcy × Dcy/Dy is set larger, but the excessive compression loss inside the high-pressure chamber becomes larger and the gap leakage becomes worse. Therefore, the parameter Hcy × Dcy/Dy needs to be set within a certain range.

Considering relation (2), the parameter 2e/Dcy is eccentricity, and in the case where the cylinder height Hcy is determined with the cylinder bore Dcy, the larger the eccentricity e, the larger the cylinder displacement. It is mentioned above that the large displacement can be achieved by increasing the eccentricity e of the crankshaft. At the time of determination at Dcy, if 2e/Dcy is set to be larger, e will be larger, but the increase of e will increase the centrifugal force of the slide, and there is a problem that the slide is separated from the piston contact to generate the slide sound. The parameter 2e/Dcy needs to be set within a certain range.

Consider relational expression (1) and (2) simultaneously, set up the specific value of the product of cylinder height Hcy and cylinder bore Dcy and casing internal diameter Dy between 15.5 to 16.5mm, set up the specific value of two times bent axle eccentric quantity e and cylinder bore Dcy between 0.2 to 0.23, can realize little casing internal diameter like this, the pump body structure of big discharge capacity, improve over compression loss and clearance and reveal, avoid the gleitbretter to break away from the problem that the piston contact produced the gleitbretter sound simultaneously.

Considering the relation (3), the parameter 2 × (e + L)/Dcy needs to be set within a certain range. If the parameter 2 × (e + L)/Dcy is set too large, it can be understood that e or L is set to be large under the condition of no change in Dcy, when the sliding vane 360 is fully extended, the part of the sliding vane 360 left in the sliding chute 322 is too long, which causes the contact area between the sliding vane 360 and the inner wall of the sliding chute 322 to be too large, meanwhile, the sliding chute 322 is axially through the cylinder 320, the sliding vane 360 contacts with the end surface of the main bearing 310 or the auxiliary bearing 340, so that the contact area between the sliding vane 360 and the surrounding structure is large, and the piston 350 drives the sliding vane 360 to move back and forth, which increases the power consumption.

If the parameter 2 × (e + L)/Dcy is set too small, it can be understood that e or L is set to be smaller under the condition of no change in Dcy, when the piston 350 rotates to the bottom dead center, the sliding piece 360 completely extends out of the sliding slot 322, the part of the sliding piece 360 left in the sliding slot 322 is too short, the surface pressure (P) formed by the sliding piece 360 and the inner wall of the sliding slot 322 when the sliding piece is loaded becomes larger, further the PV value is deteriorated, the power consumption is increased due to the little deterioration, and the sliding piece 360 is blocked in the sliding slot 322 due to the pressure difference between the two sides of the high-pressure cavity and the low-pressure cavity due to too much deterioration, so that the. It should be noted that the power consumption of the slider 360 is considered by the PV value and the oil film thickness. In the PV value, P is a surface pressure when the slider 360 and the inner wall of the chute 322 are loaded, and V is a linear velocity when the slider 360 moves.

Considering relation (4), the parameter r × T/L needs to be set within a certain range. If the parameter r T/L is set too large, it can be understood that r or T is set to be larger under the condition that L is not changed, and the increase of both is not beneficial to the reliable sliding of the sliding sheet 360. When r is large, the case where the radius r of the slider head is largest can be understood as a slider head having a flat surface, and in this case, when the piston 350 is rotated to the left and right limit positions, the outer peripheral surface of the piston 350 is easily scratched by the corner of the slider 360 head. When the thickness T of the slip sheet is larger, the upper end surface and the lower end surface of the slip sheet 360 are in contact with the end surfaces of the main bearing 310 or the auxiliary bearing 340, the contact surface is too large, and the shearing power consumption of lubricating oil is large; in addition, the mass of the sliding piece 360 is increased, the inertia force is increased, the piston 350 needs to overcome the inertia force to do work, and the power consumption of the driving motor 200 is increased.

If the parameter r × T/L is set too small, it can be understood that r is set smaller without L being changed. When r is less, the head of the slip sheet 360 is an arc surface, the smaller the radius r of the head of the slip sheet is, the larger the Hertz stress with the outer peripheral surface of the piston 350 is, metal fatigue of the outer peripheral surfaces of the slip sheet 360 and the piston 350 can be caused, and further power consumption is influenced.

The ratio of the sum of the eccentric quantity e and the sliding piece length L to the inner radius (Dcy/2) of the cylinder is set to be 1.13-1.17, the ratio of the product of the sliding piece head radius r and the sliding piece thickness T to the sliding piece length L is set to be 0.74-0.8 mm, the sliding piece sound problem of the compressor under the working condition of low frequency and low pressure difference can be effectively solved, the metal fatigue of the sliding piece 360 and the outer peripheral surface of the piston 350 after long-term contact is reduced, the power consumption can be reduced, and the performance of normal use is achieved.

In another embodiment of the application, the inner diameter Dy of the housing is in the range of 100 to 110mm, in particular if desired. In the case of a certain wall thickness of the casing 100, such a single-cylinder compressor is compact, occupies a small space, and is low in manufacturing cost. Accordingly, the structures of the driving motor 200 and the compression mechanism 300 provided in the housing 100 are relatively small, so that the manufacturing cost is low. In addition, the single cylinder compressor housing 100 height can be referenced to existing same displacement, two cylinder compressor arrangements and ensure operational performance. Compared with a double-cylinder compressor with the same displacement, the inner diameter Dy of the shell of the single-cylinder compressor is reduced, and the whole shell 100 is slender and compact.

In another embodiment of the present application, the cylinder height Hcy ranges from 30 to 36 mm; the cylinder has an inner diameter Dcy in the range of 46 to 48mm and the eccentric e of the crankshaft in the range of 4 to 5.5mm, as required. By adopting the scheme, the single-cylinder compressor can obtain larger displacement and achieve the performance of normal use. Compared with a double-cylinder compressor with the same displacement, the single-cylinder compressor has the advantages that the cylinder height Hcy is set to be larger, and the cylinder inner diameter Dcy is set to be smaller, so that the sufficient displacement can be guaranteed.

In another embodiment of the present application, the inner diameter Dy of the housing ranges from 100 to 110 mm; the cylinder height Hcy ranges from 30 to 36 mm; the cylinder has an inside diameter Dcy in the range of 46 to 48mm, with particular settings as required. The single-cylinder compressor adopting the configuration can meet the requirements of large displacement and miniaturization, can improve the input force of the compressor and achieve the performance of normal use.

In another embodiment of the present application, the inner diameter Dy of the housing is 101mm, the cylinder height Hcy is 36mm, the inner diameter Dcy of the cylinder is 46mm, and the eccentric amount e of the crankshaft is 5.2mm, as required. The single-cylinder compressor adopting the configuration can meet the requirements of large displacement and miniaturization, can further improve the input force of the compressor, and achieves better cost performance.

In another embodiment of the present application, the inner diameter Dy of the housing is 101mm, the cylinder height Hcy is 32mm, the inner diameter Dcy of the cylinder is 46mm, and the eccentric amount e of the crankshaft is 4.6 mm. The single-cylinder compressor adopting the configuration can meet the requirements of large displacement and miniaturization, can further improve the input force of the compressor, and achieves better cost performance.

In another embodiment of the present application, the ratio of the product of the cylinder height Hcy and the cylinder bore Dcy to the housing bore Dy is 16.3 mm. By adopting the scheme, the single-cylinder compressor can meet the requirements of large displacement and miniaturization.

In another embodiment of the present application, when the relations (1) and (2) are satisfied, the displacement of the cylinder 320 is set to be 20 to 25cc, and the compressor satisfies the requirement of large displacement.

In another embodiment of the present application, the slide length L ranges from 18.5 to 22.5mm, the slide thickness T ranges from 2.8 to 4mm, and the head radius of the slide ranges from 3 to 6mm, as desired. By adopting the slip sheet, the problem of slip sheet sound of the compressor under the working condition of low frequency and low pressure difference can be further effectively solved, metal fatigue of the outer peripheral surfaces of the slip sheet 360 and the piston 350 after long-term contact is reduced, power consumption can be reduced, and the performance of normal use is achieved.

In another embodiment of the present application, the slide length L is 21.5 mm; the thickness T of the slip sheet is 4 mm; the radius of the head of the slide is 4 mm. By adopting the slip sheet, the problem of slip sheet sound of the compressor under the working condition of low frequency and low pressure difference can be further effectively solved, metal fatigue of the outer peripheral surfaces of the slip sheet 360 and the piston 350 after long-term contact is reduced, power consumption can be reduced, and the performance of normal use is achieved.

In another embodiment of the present application, the head of the slip sheet 360 is provided with a hard film; alternatively, the entire surface of the slip sheet 360 is provided with a hard film. By adopting the scheme, the wear resistance of the sliding sheet 360 can be improved, and the reliability is improved.

In order to verify the performance of the single-cylinder compressor satisfying the relations (1) to (3), the power consumption of the side face of the slide is detected under the condition of changing the ratio of the sum of the eccentric amount and the length of the slide to the inner radius of the cylinder, and a curve relation graph of 2 x (e + L)/Dcy and the power consumption of the side face of the slide shown in FIG. 7 is obtained. In the single cylinder compressor, the inner diameter Dy of the housing is 101mm, the cylinder height Hcy is 32mm, the inner diameter Dcy of the cylinder is 46mm, and the eccentricity e of the crankshaft is 4.6 mm. As can be seen from FIG. 7, in the process of increasing the ratio of the sum of the eccentricity and the vane length to the inner radius of the cylinder from 1.1mm to 1.18mm, the side power consumption of the vane is firstly reduced from 65W to 38W slowly and then increased to 50W quickly. When the ratio of the sum of the eccentric amount and the length of the sliding vane to the inner radius of the cylinder is set to be 1.13-1.17, the power consumption of the side face of the sliding vane is 38-45W, the power consumption is low, and the improvement of the power of the compressor is facilitated.

In order to verify the performance of the single-cylinder compressor meeting the relation (4), the compressor is enabled to work under the low frequency of 9Hz, the force of the sliding vane is analyzed, the sliding vane is subjected to the inertia force, the spring force, the damping force, the gas force and the friction force, the force analysis graph of the sliding vane shown in figure 5 at the low frequency of 9Hz is obtained, and the curve graph of the resultant force of the sliding vane shown in figure 6 at the low frequency of 9Hz is further obtained. It can be known from fig. 6 that when the ratio of the product of the radius of the sliding piece head and the thickness of the sliding piece to the length of the sliding piece is set to be 0.74-0.8 mm, the resultant force value borne by the sliding piece is greater than 0, which indicates that the sliding piece and the piston are not separated from contact all the time under the working condition of the minimum pressure difference of low frequency 9Hz, so that the problem of sliding piece sound can be solved.

In another embodiment of the present application, there is provided a heat exchange working apparatus including the single cylinder compressor described above. The heat exchange working equipment can be an air conditioner, a refrigerator or other cooling and heating equipment. In the single-cylinder compressor, when working, the driving motor 200 drives the crankshaft 330 to rotate, so that the piston 350 arranged outside the eccentric part of the crankshaft moves in the cylinder 320, the sliding sheet 360 is elastically and slidably mounted in the sliding groove 322 of the cylinder 320, and the head of the sliding sheet 360 abuts against the outer peripheral surface of the piston 350, thereby compressing and discharging the refrigerant. The ratio of the product of the cylinder height Hcy and the cylinder inner diameter Dcy to the shell inner diameter Dy is set to be between 15.5 and 16.5mm, and the ratio of the two times of crankshaft eccentricity e to the cylinder inner diameter Dcy is set to be between 0.2 and 0.23, so that the pump body structure with small shell inner diameter and large displacement can be realized, and the compression loss and leakage are improved. The ratio of the sum of the eccentric quantity and the sliding piece length L to the inner radius (Dcy/2) of the cylinder is set to be 1.13-1.17, and the ratio of the product of the sliding piece head radius r and the sliding piece thickness T to the sliding piece length L is set to be 0.74-0.8 mm, so that the sliding piece sound problem of the compressor under the working condition of low frequency and low pressure difference can be effectively solved, the power consumption can be reduced, and the performance of normal use can be achieved. The heat exchange working equipment with the single-cylinder compressor has ensured use performance.

The present invention is not intended to be limited to the particular embodiments shown and described, but is to be accorded the widest scope consistent with the principles and novel features herein disclosed.

Claims

1. A single cylinder compressor comprising:

a housing;

the driving motor is arranged in the shell; and

15.5mm≤Hcy×Dcy/Dy≤16.5mm；

it is characterized in that the ratio of e/Dcy is more than or equal to 0.2 and less than or equal to 0.23;

1.13≤2×(e+L)/Dcy≤1.17；

0.74mm≤r×T/L≤0.8mm。

2. the single cylinder compressor of claim 1, wherein the inner diameter of said housing ranges from 100 to 110 mm.

3. The single cylinder compressor of claim 2, wherein said cylinder has a height ranging from 30 to 36 mm; the inner diameter of the cylinder ranges from 46 to 48 mm; the eccentricity of the crankshaft ranges from 4 to 5.5 mm.

4. The single cylinder compressor of claim 3, wherein the internal diameter of said housing is 101mm, the height of said cylinder is 36mm, the internal diameter of said cylinder is 46mm, and the eccentricity of said crankshaft is 5.2 mm;

5. The single cylinder compressor of claim 3, wherein the ratio of the product of the height of said cylinder and the inside diameter of said cylinder to the inside diameter of said housing is 16.3 mm.

6. The single cylinder compressor of claim 1, wherein said vane has a length in the range of 18.5 to 22.5 mm; the thickness of the slip sheet ranges from 2.8 to 4 mm; the radius of the head of the slide is in the range 3 to 6 mm.

7. The single cylinder compressor of claim 6, wherein said vane is 21.5mm in length; the thickness of the slip sheet is 4 mm; the radius of the head of the slide is 4 mm.

8. The single cylinder compressor of claim 6, wherein the head of said slide is provided with a hard membrane; or the whole surface of the sliding sheet is provided with a hard film.

9. The single cylinder compressor of any one of claims 1 to 8, wherein the cylinders have a displacement of 20 to 25 cc.

10. A heat exchange working apparatus comprising a single cylinder compressor as claimed in any one of claims 1 to 9.