WO2017088586A1

WO2017088586A1 - Multi-tank dual-stage enthalpy increasing compressor and air conditioner, heat pump water heater and control method

Info

Publication number: WO2017088586A1
Application number: PCT/CN2016/100801
Authority: WO
Inventors: 黄辉; 胡余生; 魏会军; 杨欧翔; 王珺; 余冰; 苗朋柯; 王明华
Original assignee: 珠海格力电器股份有限公司
Priority date: 2015-11-23
Filing date: 2016-09-29
Publication date: 2017-06-01
Also published as: CN105298840B; KR102122141B1; CN105298840A; KR20180079393A; JP2018531347A; JP6987754B2

Abstract

A multi-tank dual-stage enthalpy increasing compressor comprises a lower cover plate (10), a lower flange (9), an upper division plate (4), a middle division plate (5), and at least one middle cavity volume formed between each pair of the lower cover plate (10) and the lower flange (9), and the upper division plate (4) and the middle division plate (5). A total middle cavity volume is a sum of all middle cavity volumes. A ratio of a product of a volume ratio and the total middle cavity volume or one volume of the total middle cavity volume to the square of a secondary tank output volume is within a specified range. An air withdrawal volume ratio is a ratio of a secondary stage air withdrawal volume to a primary stage air withdrawal volume. The compressor provides stable air withdrawal at a secondary tank and smooth air release at a primary tank in a dual-tank or triple tank arrangement by configuring reasonable middle cavity volumes, effectively improving a problem in which a pressure fluctuation of an internal cold forming agent in a dual-stage compressor tank is too large, thus achieving smooth operation performance, and reducing a noise of the compressor. Also provided are an air conditioner or heat pump water heater of the compressor, and a compressor control method controlling the compressor.

Description

Multi-cylinder two-stage enhanced compressor and air conditioner, heat pump water heater and control method thereof

This application claims the priority of the Chinese patent application filed on November 23, 2015, the Chinese Patent Office, the application number is 201510819605.8, and the invention name is “multi-cylinder two-stage compressor and air conditioner, heat pump water heater and control method”. The entire contents of this application are incorporated herein by reference.

Technical field

The invention belongs to the technical field of air conditioners, and particularly relates to a multi-cylinder two-stage booster compressor, an air conditioner having the same, a heat pump water heater and a control method thereof.

Background technique

With the development of technology, the two-stage booster compressor has become more and more important in the fields of air conditioners, water heaters, refrigeration and refrigeration due to its high efficiency in low temperature conditions, but the existing two-stage enhancement The compressor is basically in the form of a double cylinder, and the displacement is limited in the case where the refrigeration capacity is high under low temperature conditions. Therefore, the use of multi-cylinder two-stage reinforced variable-capacity compressors has become an inevitable trend. The low-pressure stage of the multi-cylinder two-stage booster compressor has two or more compression mechanisms, at least one of which can be loaded or unloaded by the switching structure, thereby achieving two high and low pressure volume ratio switching operations, achieving Customized thermal capacity is the best energy efficiency, and low temperature heating improves the heating capacity under the premise of ensuring energy efficiency.

For a multi-cylinder two-stage booster compressor, the intermediate chamber is a chamber in which the first-stage compression and exhaust gas are mixed. Due to the periodicity of the intake and exhaust of the rolling rotor compressor, and the difference in the working phase angle between the cylinders, the intermediate cavity is too small, which will cause the pressure fluctuation of the refrigerant inside the pump body to be excessively large, thus producing the performance and noise of the compressor. Adverse effects; and the large intermediate cavity will bring certain design and process difficulties, so it is necessary to design a reasonable intermediate cavity volume.

Since the multi-cylinder two-stage booster compressor in the prior art has excessive pressure fluctuation of the internal refrigerant, thereby adversely affecting the performance, noise, and the like of the compressor, and technical problems that are difficult in design and process, the present invention studies A multi-cylinder two-stage booster compressor and an air conditioner and heat pump water heater therewith and a control method of the same are designed.

Summary of the invention

Therefore, the technical problem to be solved by the present invention is to overcome the defects in the prior art two-stage compressor that the pressure fluctuation of the refrigerant inside the cylinder is excessively large, thereby adversely affecting the performance, noise, and the like of the compressor, thereby providing a A multi-cylinder two-stage enhanced compressor and an air conditioner and heat pump water heater therewith and a control method of the same.

The present invention provides a multi-cylinder two-stage enthalpy compressor comprising a lower cover, a lower flange, an upper partition and a middle partition, and at least one intermediate chamber volume formed between the two components, the total intermediate The chamber volume is the sum of all intermediate chamber volumes, and the ratio of the product of one of the intermediate chamber volume or the total intermediate chamber volume to the volume ratio and the square of the secondary cylinder displacement is specified Within the ratio range, the volume ratio is the ratio of the secondary inspiratory volume to the primary inspiratory volume.

Preferably, when the compressor is a two cylinder, the specified ratio ranges from 0.05 to 0.20.

Preferably, when the compressor is a three cylinder, the specified ratio ranges from 0.1 to 0.3.

Preferably, the lower cover and the lower flange form a first intermediate cavity, the upper partition and the middle partition form a second intermediate cavity, and the total intermediate cavity volume is the first intermediate cavity volume and the second The sum of the volumes of the intermediate chambers.

Preferably, the total volume of the intermediate chamber comprises two intermediate chamber volume: volume _V of the first intermediate chamber and second intermediate chamber _a volume _{V 2,} the intermediate chamber and the total volume _V = V ₁ + V _2.

Preferably, when the compressor is a two-cylinder, V _{2 *} K ₁ _in the range of 0.05 to 0.20 times of ² V, wherein V is a two-cylinder displacement, K ₁ is the ratio of cylinder volume.

Preferably, when the compressor is a three cylinder, V _{in *} K ₂ is V 0.1 ~ 0.3 times of ^2, wherein V is a two-cylinder displacement, K ₂ is a three-cylinder volume ratio.

Preferably, a pin hole is provided on the lower flange, and a pin is further disposed inside the pin hole.

Preferably, the lower cover plate is provided with a first communication hole at one end of the pin hole, and the lower flange is provided with a second communication hole communicating with the other end of the first communication hole. The other end of the second communication hole is connected to a low pressure suction port of the compressor.

The present invention also provides an air conditioner or heat pump water heater comprising the aforementioned multi-cylinder two-stage booster compressor.

The invention also provides a control method for a multi-cylinder two-stage booster compressor, which is controlled and regulated for the aforementioned multi-cylinder two-stage booster compressor.

Preferably, when the compressor includes a pin, a slide plate and a lower cylinder, (1) when the compressor is operated under a light load rated condition, the pin is locked to the slide piece, so that the lower cylinder is unloaded, thereby realizing the two-cylinder mode. (2) When the compressor is operated under heavy load and low temperature conditions, the pin is unlocked, and when the lower cylinder is operated, the three-cylinder mode is operated.

The multi-cylinder two-stage enhanced compressor, air conditioner, water heater and control method provided by the invention have the following Beneficial effects:

1. By designing a reasonable intermediate cavity volume, the two-cylinder and the three-cylinder mode can achieve stable air intake, which is beneficial to smooth discharge of the first-stage cylinder, and can effectively improve the pressure fluctuation of the refrigerant inside the cylinder of the two-stage compressor. Excessive technical problems, resulting in smooth running performance of the compressor and reduced noise of the compressor;

2. Thereby effectively improving the volumetric efficiency of the compressor, achieving high efficiency and energy saving of the multi-cylinder two-stage booster compressor;

3. By designing a reasonable intermediate cavity volume, it is also possible to effectively avoid the design and process difficulties caused by the excessively large intermediate cavity;

4. The combination of the pin and the slide can effectively control the simple and quick switching and convenient operation of the compressor in the two-cylinder mode and the three-cylinder mode.

DRAWINGS

1 is a schematic structural view of a multi-cylinder two-stage enthalpy compressor according to the present invention;

2 is a graph showing the performance change rule of the multi-cylinder two-stage enthalpy compressor of the present invention in the two-cylinder mode operation;

Fig. 3 is a graph showing the performance variation of the multi-cylinder two-stage booster compressor of the present invention in a three-cylinder mode operation.

The reference numerals in the figure are indicated as:

1—Crankshaft, 2—upper flange, 3—upper cylinder, 4—upper diaphragm, 5-intermediate diaphragm, 6-medium cylinder, 7-lower diaphragm, 8-down cylinder, 9-lower flange, 10 - Lower cover.

detailed description

As shown in FIG. 1, the present invention provides a multi-cylinder two-stage enhanced compressor including a lower cover, a lower flange, an upper partition and a middle partition, and an intermediate portion formed by at least one of the foregoing two members. Cavity volume, total intermediate lumen volume is the sum of all intermediate lumen volumes, and one of the total intermediate lumen volume or the total intermediate lumen volume (ie, any intermediate lumen volume and total intermediate lumen volume) The ratio between the product of a) and the volume ratio and the square of the secondary (ie the two-stage cylinder displacement mentioned above) is within a specified ratio, wherein the volume ratio is the secondary inhalation and the primary inspiratory volume. Ratio.

By setting the above relationship of several parameters, a reasonable intermediate cavity volume can be designed, so that the two-cylinder in the two-cylinder and three-cylinder modes can be smoothly inhaled, which facilitates smooth discharge of the first-stage cylinder (see Figure 2 - 3, the performance of the compressor within the specified ratio range is stable), can effectively improve the two-stage compressor The technical problem of excessive pressure fluctuation of the refrigerant inside the cylinder effectively makes the running performance of the compressor stable and reduces the noise of the compressor; it can also improve the volumetric efficiency of the compressor, and realize the high efficiency and energy saving of the multi-cylinder two-stage booster compressor. Larger; the above-mentioned reasonable intermediate cavity volume can also effectively avoid the design and process difficulties caused by the excessively large intermediate cavity.

Preferably, when the compressor is a two cylinder, the specified ratio ranges from 0.05 to 0.20. In this way, the compressor is in the two-cylinder operation mode, and the secondary cylinder of the compressor is inflated smoothly, which facilitates smooth discharge of the first-stage cylinder, and the compressor can smoothly operate, effectively reducing noise. The above range of values is a superior range of values obtained after a large number of experiments and simulations, and a better technical effect is obtained.

Preferably, when the compressor is a three cylinder, the specified ratio ranges from 0.1 to 0.3. In this way, the compressor is in the three-cylinder operation mode, and the secondary cylinder of the compressor is inflated smoothly, which facilitates smooth discharge of the first-stage cylinder, and the compressor can smoothly operate, thereby effectively reducing noise. The above range of values is a superior range of values obtained after a large number of experiments and simulations, and a better technical effect is obtained.

Preferably, the lower cover and the lower flange form a first intermediate cavity, the upper partition and the middle partition form a second intermediate cavity, and the total intermediate cavity volume is the first intermediate cavity volume and the second The sum of the volumes of the intermediate chambers. The positional relationship between the first intermediate cavity and the second intermediate cavity is specifically defined by the above structure, which provides a prerequisite for stable suction of the secondary cylinder, smooth exhaust of the primary cylinder, and smooth operation of the compressor.

Preferably, the total volume of the intermediate chamber comprises two intermediate chamber volume: volume _V of the first intermediate chamber and second intermediate chamber _a volume _{V 2,} the intermediate chamber and the total volume _V = V ₁ + V _2. This is a preferred embodiment, which provides a prerequisite for stable suction of the secondary cylinder, smooth exhaust of the primary cylinder, and smooth operation of the compressor.

Preferably, when the compressor is a two-cylinder, V _{2 *} K ₁ _in the range of 0.05 to 0.20 times of ² V, wherein V is a two-cylinder displacement, K ₁ is the ratio of cylinder volume. By the proportional relationship and the numerical range, the relationship between the second intermediate chamber volume and the two-cylinder displacement and the two-cylinder volume ratio in the two-cylinder mode is defined, thereby designing a reasonable intermediate chamber volume, thereby causing the compressor to operate. The performance is stable, the noise of the compressor is reduced, the compressor volumetric efficiency can be effectively improved, and the multi-cylinder two-stage booster compressor can be more efficient and energy-saving.

Preferably, when the compressor is a three cylinder, V _{in *} K ₂ is V 0.1 ~ 0.3 times of ^2, wherein V is a two-cylinder displacement, K ₂ is a three-cylinder volume ratio. Through the proportional relationship and the numerical range, the relationship between the total intermediate cavity volume and the two-cylinder displacement and the three-cylinder volume ratio in the three-cylinder mode is defined, thereby designing a reasonable intermediate cavity volume, thereby making the compressor operating performance. It can smoothly reduce the noise of the compressor; it can also effectively improve the volumetric efficiency of the compressor, and realize the high efficiency and energy saving of the multi-cylinder two-stage booster compressor. What needs to be explained here is that the total intermediate chamber volume is selected in the case of the three cylinders, and the second intermediate chamber volume is selected in the two cylinders because the first and second intermediate chamber volumes correspond to the lower cylinders, respectively. And medium cylinders (both are low pressure cylinders). In the double cylinder operation, only the middle cylinder is actually working due to the lower cylinder unloading. Although the first and second intermediate chambers are communicated through the flow holes, considering the actual throttling effect of the flow holes (the diameter of which is small), the first intermediate chamber has little effect on reducing the pressure fluctuation of the middle cylinder, so the double cylinder The second intermediate chamber volume is mainly considered; while the three-cylinder current cylinder and the middle cylinder are both working, the first intermediate chamber and the second intermediate chamber need to be considered for reducing the pressure fluctuation of the middle cylinder and the lower cylinder, so the three cylinders need to be considered. Total intermediate chamber volume.

Preferably, a pin hole (not shown) is disposed on the lower flange, and a pin (not shown) is further disposed inside the pin hole. The pin of the lower cylinder can be locked or loosened by the pin, thereby functioning to unload or start the lower cylinder.

Preferably, the lower cover plate is provided with a first communication hole at one end of the pin hole, and the lower flange is provided with a second communication hole communicating with the other end of the first communication hole. The other end of the second communication hole is connected to a low pressure suction port of the compressor. By providing the first communication hole and the second communication hole described above, the gas leaking from the pin hole can be effectively introduced into the low pressure suction port of the compressor, thereby effectively preventing the leakage of the refrigerant inside the compressor and maintaining the leakage. Stable pressure.

The present invention also provides an air conditioner or heat pump water heater comprising the aforementioned multi-cylinder two-stage booster compressor. The air conditioner or the heat pump water heater including the multi-cylinder two-stage booster compressor described above can design a reasonable intermediate volume of the compressor by setting the above relationship of several parameters, thereby making the two-cylinder and the three-cylinder The two-stage cylinder in the mode is stable in suction, which facilitates the smooth exhaust of the first-stage cylinder (see Figure 2-3, the compressor performance is stable within the specified ratio range), which can effectively improve the internal refrigerant of the two-stage compressor cylinder. The pressure fluctuations are too large technical problems, so that the compressor's running performance is stable and the compressor noise is reduced; the compressor volumetric efficiency can be improved, and the multi-cylinder two-stage booster compressor can be more efficient and energy-saving; By designing the above reasonable intermediate cavity volume, it is also possible to effectively avoid the design and process difficulties caused by the excessively large intermediate cavity. Thereby improving the running performance of the air conditioner and the heat pump water heater.

The invention also provides a control method for a multi-cylinder two-stage booster compressor, which is controlled and regulated for the aforementioned multi-cylinder two-stage booster compressor. This can make the two-cylinder in the two-cylinder and three-cylinder modes inhale. Stable, which facilitates smooth discharge of the first-stage cylinder (see Figure 2-3, the compressor performance is stable within the specified ratio range), which can effectively improve the technical problem of excessive pressure fluctuation of the refrigerant inside the cylinder of the two-stage compressor. Therefore, the compressor's running performance is stabilized and the compressor noise is reduced. The compressor volumetric efficiency can also be improved, and the multi-cylinder two-stage booster compressor can be more efficient and energy-saving. The cavity volume can also effectively avoid the design and process difficulties caused by the excessively large intermediate cavity.

Preferably, when the compressor includes a pin, a slide plate and a lower cylinder, (1) when the compressor is operated under a light load rated condition, the pin is locked to the slide piece, so that the lower cylinder is unloaded, thereby realizing the two-cylinder mode. (2) When the compressor is operated under heavy load and low temperature conditions, the pin is unlocked, and when the lower cylinder is operated, the three-cylinder mode is operated. The combination of the pin and the slide can effectively control the simple and quick switching and convenient operation of the compressor in the two-cylinder mode and the three-cylinder mode.

Preferred embodiments of the present invention are described below.

As shown in FIG. 1, the multi-cylinder two-stage reinforced variable-capacity compressor of the present invention has two intermediate chambers: a first intermediate chamber formed by the lower cover 10 and the lower flange 9, and an upper partition 4; A second intermediate cavity formed by the intermediate partition 5. The two are connected through the intermediate flow channel. The specific working principle of multi-cylinder two-stage reinforced variable-capacity compressor is:

The double-cylinder mode is adopted when operating under light load rated conditions. At this time, the pin locks the slide piece, the lower cylinder is unloaded, and the first-stage medium-pressure gas discharged from the middle cylinder and the supplemental gas are mixed in the intermediate cavity and the intermediate flow path to enter. Two-cylinder (upper cylinder); three-cylinder mode is used when operating under heavy load and low temperature conditions. At this time, the pin is unlocked, the lower cylinder is operated, and the medium-pressure gas and the supplementary gas discharged from the middle and lower cylinders are in the intermediate chamber. After mixing in the intermediate flow passage, it enters the secondary cylinder (upper cylinder). Further, compared with the two-cylinder mode, the flow rate of the first-stage cylinder compressed gas is larger in the three-cylinder mode, and the pressure fluctuation in the three-cylinder mode should be more significant in the case where the intermediate chamber and the intermediate flow passage volume are constant.

The technical solution provides a multi-cylinder two-stage reinforced variable-capacity compressor, a first intermediate cavity volume and a second intermediate cavity volume and a secondary cylinder displacement and volume ratio (secondary intake amount and first-stage intake amount) The ratio range of the ratio). Define 1 in the first intermediate chamber volume V, 2 in the second intermediate chamber volume V, in the intermediate chamber volume V = 1 in the V + 1 in the middle 2, the displacement in the secondary cylinder V, the ratio in the cylinder to the cylinder K1, the ratio of the three cylinders K2, setting: 2*K1 in V is 0.05~0.20 times of V2 (as shown in Fig. 2), and *K2 in V is 0.1~0.3 times of V2 (as shown in Fig. 3), which can guarantee double cylinder and three The secondary cylinder in the cylinder mode has a stable suction, which is conducive to smoothing the first-stage cylinder. The exhaust gas can effectively improve the volumetric efficiency of the compressor, and realize the high efficiency and energy saving of the multi-cylinder two-stage booster compressor.

It will be readily understood by those skilled in the art that the above advantageous modes can be freely combined and superimposed without conflict.

The above is only the preferred embodiment of the present invention, and is not intended to limit the present invention. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present invention should be included in the protection of the present invention. Within the scope. The above is only a preferred embodiment of the present invention, and it should be noted that those skilled in the art can make several improvements and modifications without departing from the technical principles of the present invention. It should also be considered as the scope of protection of the present invention.

Claims

A solar Stirling engine heat absorber protection device, the Stirling engine comprising a heat absorber, the heat sink having a lighting opening (7); wherein the protection device comprises an opaque shading a plate (6), the light shielding plate (6) is rotatably connected to the heat absorber casing (3), so that the light shielding plate (6) is rotated to block the first position of the lighting opening (7), or rotate To a fourth position in which the lighting opening (7) is fully opened, or to a second position and a third position in which the lighting opening (7) is partially opened.
A solar Stirling engine heat absorber protection device according to claim 1, further comprising a driver (1) and a rotating shaft (16) disposed on said heat absorber casing (3), said driver (1) a transmission mechanism (2) is connected between the inner end of the rotating shaft (16), and an outer end of the rotating shaft (16) is connected in parallel with the light shielding plate (6), and the rotating shaft (16) The plane of rotation is perpendicular to the central axis of the daylighting opening (7).
The solar Stirling engine heat absorber protection device according to claim 2, characterized in that: the outer side of the front end portion of the heat absorber casing (3) has an annular groove, and the annular groove has a support therein. The ring (13) extends through the front end portion of the heat absorber casing (3) and is fixed to the support ring (13).
The solar Stirling engine heat absorber protection device according to claim 3, characterized in that: the power output end of the transmission mechanism (2) is provided with a driving gear (4), and the annular groove is further provided a drive ring (11) axially positioned by the support ring (13), an outer ring surface of the drive ring (11) is provided with an outer ring gear (9) meshing with the drive gear (4);

The rotating shaft (16) is sleeved with a driven gear (18), and an inner ring surface of the driving ring (11) is provided with an inner ring gear (17) that meshes with the driven gear (18). .
The solar Stirling engine heat absorber protection device according to claim 4, characterized in that: the inner end of the rotating shaft (16) is connected with a lever (15), and the axis of the lever (15) The extending direction is perpendicular to the extending direction of the axis of the rotating shaft (16);

a slide ball (14) is slidably sleeved on the lever (15), a pressure ring is disposed on one side of the drive ring (11), and the slide ball (14) is located in the drive ring (11) Between the pressure ring (12), the drive ring (11) and the pressure ring (12) are fixed, and the drive ring (11) and the pressure A space is formed between the rings (12) for swinging the lever (15).
The solar Stirling engine heat absorber protection device according to claim 3, characterized in that the power output end of the driving mechanism (2) is provided with a first sprocket (10), and the rotating shaft (16) The outer end sleeve is provided with a second sprocket (20) coupled to the rotating shaft (16), and a chain (19) is connected between the first sprocket (10) and the second sprocket (20). ).
The solar Stirling engine heat absorber protection device according to claim 2, characterized in that: the power output end of the transmission mechanism (2) is provided with a driving flange (22), and the end of the rotating shaft (16) A driven flange (21) is provided, and the driving flange (22) and the driven flange (21) are integrally connected.
The solar Stirling engine heat absorber protection device according to claim 7, characterized in that the number of the light shielding plates (6) is one.
The solar Stirling engine heat absorber protection device according to any one of claims 1 to 6, characterized in that the number of the light shielding plates (6) is at least two.
The solar Stirling engine heat absorber protection device according to any one of claims 1 to 7, characterized in that the light shielding plate (6) is provided with a light reflecting layer on the front surface thereof.