A pump body assembly and a compressor

Abstract

The present invention discloses a pump body assembly and a compressor. The pump body assembly includes a crankshaft and a cylinder block having a gas replenishing port. The crankshaft has an eccentric portion located within the cylinder block, and a roller is sleeved outside the eccentric portion. When the crankshaft rotation angle θ is 150°, at least more than 2 / 3 of the effective enthalpy increase area of the gas replenishing port is closed by the roller or the sealing portion of the crankshaft. The present invention reasonably designs the position and shape of the gas replenishing port, especially the formulaic design of the gas replenishing closing angle, which not only ensures sufficient gas replenishment at the gas replenishing port but also solves the problem of gas replenishment reflux, realizing the high-efficiency operation of the compressor under single-stage enthalpy increase in all working conditions, and significantly improving the energy efficiency of the compressor.

Description

Technical Field

[0001] The present invention belongs to the field of heat exchange, and particularly relates to a pump body assembly and a compressor. Background Art

[0002] When an existing compressor is used for low-temperature heating, since the refrigerant has a low evaporation temperature, the suction density is small, resulting in a serious attenuation of the heating capacity of the compressor at low temperatures; the common method to solve the low-temperature attenuation of the compressor is the gas injection technology.

[0003] The gas injection technology includes single-stage gas injection technology and double-stage gas injection technology; among them, the double-stage gas injection technology is also called a double-stage enthalpy-increasing compressor, which has a good gas injection effect, but high cost and a complex production process. In particular, for the two cylinders of the double-stage compression, the displacement only counts the displacement of the first-stage cylinder, resulting in a limited displacement of the compressor, and severely limiting its displacement usage range. In addition, in a usage environment with a small pressure ratio (such as summer refrigeration), due to the presence of the two cylinders, at this time, due to the influence of the clearance volume, etc. on the performance of the compressor, it is more obvious, resulting in a low energy efficiency of the double-stage enthalpy-increasing compressor under the condition of a small pressure ratio.

[0004] Many existing models cannot ensure the relative independence of the gas injection port, the suction hole, and the roller inner hole cavity (the chamfer of the roller inner hole and the vacant part outside the thrust surface below the eccentric circle of the crankshaft). During a compression cycle, gas leakage that does not meet the design requirements often occurs, resulting in limited refrigerant replenishment. And a small number of models barely meet various conditions, but the gas injection port can only be opened very small, also resulting in a poor gas injection effect. Summary of the Invention

[0005] The purpose of the present invention is to provide a pump body assembly and a compressor, which can increase the area of the gas injection port, improve the gas injection and enthalpy-increasing efficiency, avoid gas injection backflow, reduce power, and improve the energy efficiency of the compressor.

[0006] To achieve the above purpose, the specific technical solutions of the pump body assembly and the compressor of the present invention are as follows:

[0007] A pump body assembly includes a crankshaft and a cylinder block; the crankshaft has an eccentric part located inside the cylinder block, and a roller is sleeved outside the eccentric part; the cylinder block is provided with a gas injection port, and when the crankshaft rotation angle θ is 150°, the area S of the part of the gas injection port that is not sealed D and the effective area S of the gas injection port E satisfy

[0008] Further, when the crankshaft rotation angle θ is 150°, the area S of the part of the gas injection port that is not sealed D satisfies S D = 0.

[0009] Further, when the crankshaft rotation angle θ is 120°, the non-sealed air intake port portion S G and the area S of the effective portion of the air intake port E , satisfy

[0010] Further, the pump body assembly further includes a sealing portion disposed on one side where at least one end face of the eccentric portion is located; the crankshaft drives the roller to rotate so that the end face of the sealing portion has an avoidance position for opening the air intake port and a closing position for closing the air intake port.

[0011] Further, the air intake port is a circular hole, a waist-shaped hole or an oval hole.

[0012] Further, the air intake port is formed by a plurality of continuous curves.

[0013] Further, the curve includes a closing curve; within one compression cycle, when the closing curve is completely closed by the roller or the sealing portion of the crankshaft, the air intake port is closed.

[0014] Further, when the crankshaft rotation angle θ is 140°, the length L of the unclosed portion of the closing curve length M and the closing curve length L J , satisfy

[0015] Further, when the crankshaft rotation angle θ is 170°, the length L of the unclosed portion of the closing curve length M and the closing curve length L J , satisfy

[0016] A compressor includes the above-mentioned pump body assembly.

[0017] The pump body assembly and the compressor of the present invention have the following advantages: increasing the area of the air intake port, enhancing the effect of air intake and enthalpy increase and efficiency improvement, avoiding air intake backflow, reducing power, and improving the energy efficiency of the compressor. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1 is a schematic diagram of the air intake port of the present invention;

[0019] Figure 2 is a schematic diagram of the boundary line of the effective area of the present invention;

[0020] Figure 3 is a schematic diagram of the relationship between the pressure in the compression chamber and the angle of the present invention (the abscissa is the crankshaft rotation angle, and the ordinate is the pressure);

[0021] Figure 4 is a schematic diagram of the closing curve of the present invention.

[0022] Explanation of the marks in the figure:

[0023] 1. Cylinder block; 2. Crankshaft; 3. Roller; 4. Gas injection port; 41. Closing curve. Detailed implementation mode

[0024] In order to better understand the purpose, structure and function of the present invention, the following further describes in detail a pump body assembly and a compressor of the present invention with reference to the accompanying drawings.

[0025] As Figure 1 shown, the compressor of the present invention is a rotary enthalpy-increasing compressor, including a pump body assembly and a motor. Driven by the motor, the pump body assembly compresses the refrigerant and drives the entire refrigeration device to work.

[0026] The pump body assembly includes a cylinder block 1, a crankshaft 2 and a roller 3. The cylinder block 1 has a suction hole and a gas injection port 4. The crankshaft 2 has an eccentric part, which is arranged in the cylinder block 1. The roller 3 is sleeved outside the eccentric part and rolls in the cylinder block 1 along with the eccentric part.

[0027] Embodiment 1

[0028] When the crankshaft rotation angle θ is 150°, at least more than 2 / 3 of the effective enthalpy-increasing area of the gas injection port 4 is closed by the roller 3; more preferably, the gas injection port 4 is completely closed.

[0029] In order to meet the above requirements for the positional relationship of the gas injection port 4, when the crankshaft 2 rotation angle θ is 150°, the area S D of the un-sealed part of the gas injection port and the area S E of the effective part of the gas injection port satisfy where the effective part of the gas injection port, that is, during the operation of the compressor, the gas injection port 4 will be opened by the roller and the part that can contact the cylinder compression chamber.

[0030] Combined with Figure 1 shown, in order to calculate the area S D of the un-sealed part of the gas injection port when the crankshaft 2 rotation angle θ is 150°, the un-sealed part area D of the gas injection port and the area A of the gas injection port, and the area B outside the outer circle of the roller when the crankshaft rotation angle θ is 150° satisfy D = A ∩ B.

[0031] Among them, the point (x, y) located in the area B outside the outer circle of the roller when the crankshaft 2 rotation angle θ is 150° satisfies where R is the outer circle radius of the roller 3 and e is the eccentricity of the roller 3.

[0032] represents the curve equation of the outer circle of the roller 3 when the crankshaft 2 rotation angle θ is 150°. When the crankshaft 2 rotation angle θ is 150°, the center of the outer circle of the roller 3 is denoted as point A, and the coordinates are (x1, y1), then y1 = tan[90° - (180° -

[0033] Therefore, when the crankshaft 2 rotates by an angle θ of 150°, the curve equation of the outer circle of the roller 3 is as follows: where R is the radius of the outer circle of the roller 3, and e is the eccentricity of the roller 3.

[0034] Combined with Figure 2 as shown, in order to calculate the area S of the effective part of the gas replenishing port when the crankshaft 2 rotates by an angle θ of 150°, E , the effective part area E of the gas replenishing port, the area A of the gas replenishing port, and the area C outside the inner circle swept by the roller satisfy E = A ∩ C.

[0035] Among them, for the points (x, y) in the area C outside the inner circle swept by the roller, x 2 + y 2 ≥ (R - e) 2 .

[0036] x 2 + y 2 ≥ (R - e) 2 , represents a circle with the cylinder center as the origin and (R - e) as the radius; this circle is the trajectory drawn by the point on the outer circle of the roller 3 that is closest to the cylinder center when it rotates one week. The area inside the circle will never be opened by the roller 3, so the gas replenishing port opened inside the circle is an ineffective gas replenishing port area; on the contrary, there is a certain angle in the area outside the circle, and this area will be exposed to the inner cavity of the cylinder, and the gas replenishing port opened in this area is an effective gas replenishing port area.

[0037] In the prior art, in order to ensure the enthalpy increase effect, it is necessary to ensure sufficient gas replenishing volume, so the gas replenishing port 4 needs to be opened larger, which requires a larger closing angle of the roller 3 to the gas replenishing port 4 to ensure that the area of the gas replenishing port 4 is large enough. However, on the contrary, when the closing angle of the roller 3 to the gas replenishing port 4 is large, when the enthalpy increase pressure in the compression cavity is such that the pressure in the compression cavity is greater than the gas replenishing pressure, the phenomenon of gaseous refrigerant in the compression cavity flowing back to the gas replenishing port 4 will occur, resulting in the refrigerant being compressed back and forth, generating useless power, thereby reducing the energy efficiency.

[0038] In this application, the gas replenishing port 4 is opened in the area covered by the inner circle of the roller 3, which greatly increases the available opening area of the gas replenishing port 4. Therefore, the balance of the relationship between the area and the closing angle of the gas replenishing port 4 is broken. Moreover, further, the energy efficiency is optimal when the gas replenishing port 4 closes the suction hole at 150° or even earlier.

[0039] According to design experience, when the area of the gas replenishing port 4 is closed to 1 / 3, due to the small area, and the unclosed part of the gas replenishing port 4 is generally a long and narrow structure, it is generally defaulted that no refrigerant in the compression cavity will enter the gas replenishing port 4, which affects the energy efficiency of the compressor.

[0040] As Figure 3 shown, taking the research of a 15.0cc displacement enhanced enthalpy compressor on a heat pump hot air blower and the compressor experimental data as an example, the solution is described. For this compressor under the rated heating condition, it is a graph showing the relationship between the suction cavity of the compressor, the pressure in the compressor cavity and the enhanced enthalpy pressure. It can be seen that when the crankshaft angle is close to 150°, the pressure in the compression cavity of the compressor is close to the enhanced enthalpy pressure. At this time, the enhanced enthalpy port needs to be closed to prevent the refrigerant in the compressor cavity from flowing back to the enhanced enthalpy hole.

[0041] Embodiment 2

[0042] When the crankshaft 2 rotation angle θ is 120°, at least more than 1 / 3 of the effective enhanced enthalpy area of the gas injection port 4 is not closed by the roller 3.

[0043] In order to meet the requirements of the above gas injection port 4 position relationship, when the crankshaft 2 rotation angle θ is 120°, the unsealed part S of the gas injection port G and the area S of the effective part of the gas injection port E , satisfy Closing the gas injection port too early will result in too small an opening area of the gas injection port and too small a gas injection angle, thus making the effect of enhancing enthalpy and efficiency of gas injection not good.

[0044] For calculation, when the crankshaft 2 rotation angle θ is 120°, the area S of the unsealed part of the gas injection port G , the unsealed part area G of the gas injection port and the area A of the gas injection port, and the area F outside the outer circle of the roller when the crankshaft rotation angle θ is 120°, satisfy G = A ∩ F.

[0045] Among them, for the point (x, y) located in the area F outside the outer circle of the roller when the crankshaft 2 rotation angle θ is 120°, it satisfies

[0046] represents the curve equation of the outer circle of the roller when the crankshaft 2 rotation angle θ is 120°, and F represents the points outside the outer circle of the roller.

[0047] In order to achieve the above design of the gas injection port 4, in addition to being sealed by the roller, the gas injection port 4 can also be sealed by a sealing part. The sealing part is arranged on at least one side where the end face of the eccentric part is located. The crankshaft 2 drives the roller 3 to rotate so that the end face of the sealing part and a part of the end face of the roller 3 have an avoidance position for opening the gas injection port 4 and a closing position for closing the gas injection port 4, or the end face of the sealing part has an avoidance position for opening the gas injection port 4 and a closing position for closing the gas injection port 4. For the specific setting of the sealing part, reference can be made to the Chinese patent with the application number 201820753065.7. By combining the sealing part and the gas injection port 4 of this application, a better enhanced enthalpy gas injection effect can be achieved.

[0048] Example 3

[0049] The air inlet 4 can be a circular hole, an oval hole, an oblong hole, or a special-shaped hole formed by multiple curves, etc.

[0050] Combined Figure 4 As shown, the multiple curves include a closing curve 41. During one compression cycle, when the closing curve 41 is completely closed by the roller 3 or the sealing part of the crankshaft, the air inlet 4 is closed; when the crankshaft 2 rotates by an angle θ of 140°, more than 4 / 5 of the closing curve 41 is not closed by the roller 3; when the crankshaft 2 rotates by an angle θ of 170°, more than 4 / 5 of the closing curve 41 is closed by the roller 3.

[0051] To meet the above requirements, when the crankshaft rotation angle θ is 120°, the length L of the part of the closing curve length not closed by the roller M and the closing curve length L J , meet When the crankshaft rotation angle θ is 120°, the length L of the part of the closing curve length not closed by the roller M and the closing curve length L J , meet

[0052] Among them, at 120° and 170°, the part M of the closing curve length not closed by the roller, the point J on the closing curve, the point H not closed by the roller when the crankshaft rotation angle θ is 140°, and the point I closed by the roller when the crankshaft rotation angle θ is 170° satisfy M = J ∩ H ∩ I.

[0053] (x + 0.839·e) 2 +(y - 1.192·e) 2 = R 2 , that is:

[0054] {x – [-tan(180° - 140°)·e]} 2 +[y - cot(180° - 140°)·e] 2 = R 2

[0055] Denote the point B(x2, y2) as the coordinates of the center of the roller 3 when the crankshaft 2 rotates by an angle θ of 140°, then:

[0056] x2 = -tan(180° - 140°)·e = -0.839·e

[0057] y2 = cot(180° - 140°)·e = 1.192·e

[0058] Therefore, when the crankshaft 2 rotates by an angle θ of 140°, the curve equation of the outer circle of the roller 3:

[0059] (x + 0.839·e) 2 +(y - 1.192·e) 2 = R 2

[0060] Therefore, the point (x, y) that is not closed by the roller when the crankshaft 2 rotates by an angle θ of 140° satisfies (x + 0.839·e) 2 +(y - 1.192·e) 2 ≥R 2 。

[0061] The point (x, y) that is not closed by the roller when the crankshaft 2 rotates by an angle θ of 170° satisfies (x + 0.176·e) 2 +(y - 2.747·e) 2 ≤R 2 。

[0062] Comparison of experimental structures of each embodiment and comparative example

[0063] Table 1 Comparison table of energy efficiency of each component of the 3kW hot air blower system with the above pump body and compressor

[0064]

[0065]

[0066] Before improvement, when the crankshaft rotates to 200°, 2 / 3 is closed; the performance of the compressor is too poor, so the measurement is abandoned;

[0067] The comprehensive energy efficiency is calculated based on the data of the previous five working conditions according to the national standard GB 21455-2019

[0068] Thus, through geometric mathematics, the position and shape of the air supplement port 4 are reasonably designed, especially the formulaic design of the air supplement closing angle, which not only ensures sufficient air supplement at the air supplement port 4 but also solves the problem of air supplement backflow, realizes the efficient operation of the compressor under full working conditions with single-stage enthalpy increase, and significantly improves the energy efficiency of the compressor

[0069] It can be understood that the present invention is described through some embodiments. Those skilled in the art know that without departing from the spirit and scope of the present invention, various changes or equivalent replacements can be made to these features and embodiments. In addition, under the teaching of the present invention, these features and embodiments can be modified to adapt to specific situations and materials without departing from the spirit and scope of the present invention. Therefore, the present invention is not limited by the specific embodiments disclosed herein, and all embodiments falling within the scope of the claims of this application belong to the scope protected by the present invention

Claims

1. A pump body assembly, comprising a crankshaft and a cylinder block; the crankshaft has an eccentric portion located within the cylinder block, and a roller is sleeved outside the eccentric portion; characterized in that, The cylinder block is provided with an air supplement port. When the crankshaft rotation angle θ is 150°, the area S of the part of the air supplement port that is not sealed D and the effective area S of the air supplement port E , satisfy 2. The pump body assembly according to claim 1, characterized in that, When the crankshaft angle θ is 150°, the area S of the air supplement port part that is not sealed D , satisfies S D = 0.

3. The pump body assembly according to claim 1, characterized in that, When the crankshaft rotation angle θ is 120°, the area S of the part of the air inlet port that is not sealed G and the effective area S of the air inlet port E , satisfy 4. The pump body assembly according to claim 1 or 3, characterized in that, The pump body assembly further includes a sealing portion, and the sealing portion is disposed on one side where at least one end face of the eccentric portion is located; the crankshaft drives the roller to rotate, so that the end face of the sealing portion has an avoidance position for opening the air supplement port and a closing position for closing the air supplement port.

5. The pump body assembly according to claim 1, characterized in that, The air supplement port is a circular hole, a waist-shaped hole or an oval hole.

6. The pump body assembly according to claim 4, characterized in that, The air supplement port is formed by a plurality of continuous curves.

7. The pump body assembly according to claim 6, characterized in that, The curve includes a closing curve; within one compression cycle, when the closing curve is completely closed by the roller or the sealing portion of the crankshaft, the air supplement port is closed.

8. The pump body assembly according to claim 7, characterized in that, When the crankshaft angle θ is 140°, the length L of the unclosed part of the closing curve length M and the closing curve length L J , satisfy 9. The pump body assembly according to claim 7 or 8, characterized in that, When the crankshaft angle θ is 170°, the length L of the unclosed part of the closing curve length M and the closing curve length L J , satisfy 10. A compressor, characterized in that, It includes the pump body assembly according to any one of claims 1-9.

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