CN112253461B

CN112253461B - Compressor, air conditioner and water heater

Info

Publication number: CN112253461B
Application number: CN202011158973.XA
Authority: CN
Inventors: 魏会军; 黄秦; 阙沛祯; 胡艳军; 向柳; 董辉
Original assignee: Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
Current assignee: Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
Priority date: 2020-10-26
Filing date: 2020-10-26
Publication date: 2022-10-28
Anticipated expiration: 2040-10-26
Also published as: CN112253461A

Abstract

The invention provides a compressor, an air conditioner and a water heater, wherein the compressor comprises: a crankshaft; the crankshaft penetrates through the low pressure cylinder and the high pressure cylinder, and the low pressure cylinder is positioned on one side, close to a motor of the compressor, of the high pressure cylinder; the compressor is provided with an intermediate cavity, and the intermediate cavity is positioned on one side of the high-pressure cylinder close to the motor, so that the refrigerant flowing out of the low-pressure cylinder flows into the high-pressure cylinder after passing through the intermediate cavity; wherein, the ratio scope of total volume V of middle chamber and total discharge capacity K of low pressure jar is: V/K is more than or equal to 1.5 and less than or equal to 5. The compressor solves the problems that in the prior art, the two-stage enthalpy-increasing compressor has unsmooth exhaust of a low-pressure cylinder and difficult air suction of a high-pressure cylinder due to the undersize middle cavity.

Description

Compressor, air conditioner and water heater

Technical Field

The invention relates to the field of compressors, in particular to a compressor, an air conditioner and a water heater.

Background

With the development of science and technology, the double-stage enthalpy-increasing compressor still can keep efficient characteristics under low-temperature working conditions, and occupies more and more important positions in the fields of air conditioners, water heaters, freezing and refrigerating and the like, but the conventional double-stage enthalpy-increasing compressor has the problems of large noise, large vibration, low energy efficiency, incapability of meeting the requirements on reliability and the like.

In the double-stage enthalpy-increasing compressor, gas discharged by a low-pressure cylinder after first-stage compression is mixed with system air supplement, and then is sucked by a high-pressure cylinder for second-stage compression, and a middle cavity is a cavity for mixing the discharged gas and the air supplement after the first-stage compression. Because the air suction and the air exhaust of the double-stage enthalpy-increasing compressor have periodicity, and the working phase angle between the high-pressure cylinder and the low-pressure cylinder is different, if the intermediate cavity is too small, the pressure fluctuation of the refrigerant in the pump body structure is too large, and the performance, the noise and the like of the compressor are adversely affected; the too large intermediate cavity brings certain design and process difficulties.

Meanwhile, the existing double-stage enthalpy-increasing compressor is basically in a double-cylinder form, and is limited by the displacement on occasions with high requirements on refrigeration capacity under low-temperature working conditions and the like.

Disclosure of Invention

The invention mainly aims to provide a compressor, an air conditioner and a water heater, and aims to solve the problems that in the prior art, a low-pressure cylinder is not smooth in exhaust and a high-pressure cylinder is difficult to suck due to the fact that an intermediate cavity of a two-stage enthalpy-increasing compressor is too small.

In order to achieve the above object, according to a first aspect of the present invention, there is provided a compressor comprising: a crankshaft; the crankshaft penetrates through the low pressure cylinder and the high pressure cylinder, and the low pressure cylinder is positioned on one side of the high pressure cylinder, which is close to a motor of the compressor; the compressor is provided with an intermediate cavity, and the intermediate cavity is positioned on one side of the high-pressure cylinder close to the motor, so that the refrigerant flowing out of the low-pressure cylinder flows into the high-pressure cylinder after passing through the intermediate cavity; wherein, the ratio scope of total volume V of intermediate chamber and the total discharge capacity K of low pressure jar is: V/K is more than or equal to 1.5 and less than or equal to 5.

Further, the low pressure cylinder is one, and the ratio range of the total volume V of the intermediate cavity to the total displacement K of the low pressure cylinder is: V/K is more than or equal to 1.5 and less than or equal to 4.5; or the low-pressure cylinders are arranged in sequence along the direction far away from the high-pressure cylinder; the total displacement K of low pressure jar is the displacement sum of a plurality of low pressure jars, and the ratio scope of the total volume V of intermediate chamber and the total displacement K of low pressure jar is: V/K is more than or equal to 2.0 and less than or equal to 5.0.

Furthermore, the number of the low-pressure cylinders is one, and the middle cavity is arranged on one side of the low-pressure cylinder, which is far away from the high-pressure cylinder; or the middle cavity is arranged between the low pressure cylinder and the high pressure cylinder; or the middle cavity comprises a first cavity part and a second cavity part which are communicated with each other, the first cavity part is positioned on one side of the low pressure cylinder, which is far away from the high pressure cylinder, and the second cavity part is positioned between the low pressure cylinder and the high pressure cylinder; the total volume V of the intermediate chamber is the sum of the volumes of the first and second chamber portions.

Furthermore, the number of the low pressure cylinders is multiple, and the low pressure cylinders are sequentially arranged along the direction far away from the high pressure cylinder; the total displacement K of the low-pressure cylinders is the sum of the displacements of the low-pressure cylinders; the middle cavity comprises a first cavity portion and a second cavity portion which are mutually communicated, the first cavity portion is located on one side, away from the high-pressure cylinder, of the low-pressure cylinders, close to the motor, of the low-pressure cylinders, the second cavity portion is located between the low-pressure cylinders, close to the high-pressure cylinder, of the low-pressure cylinders and the high-pressure cylinder, of the low-pressure cylinders, and the total volume V of the middle cavity is the sum of the volumes of the first cavity portion and the second cavity portion.

Furthermore, along the axis direction of bent axle, a plurality of low-pressure cylinders overlap in proper order and establish on the corresponding shaft part of bent axle, are provided with intermediate bottom between two adjacent low-pressure cylinders, are provided with the intermediate intercommunicating pore that is used for communicateing the cavity of two corresponding low-pressure cylinders on the intermediate bottom.

Further, the compressor comprises an air supplementing channel, and the air supplementing channel is arranged on one of the at least one low-pressure cylinder; or the compressor comprises a plurality of air supply channels, the low-pressure cylinders are a plurality of air supply channels, and the air supply channels are arranged on the low-pressure cylinders in a one-to-one correspondence mode.

Further, the compressor further includes: the first flange is arranged on one side, close to the motor, of the low-pressure cylinder, and at least part of the middle cavity is arranged on the first flange.

Further, the first flange is provided with a first cavity part and a first opening part communicated with the first cavity part, and the first opening part is arranged towards the low-pressure cylinder; the first cavity portion is used for forming a middle cavity.

The compressor further comprises a first partition plate, the first partition plate is arranged opposite to the first opening part, and a first communication hole for communicating the cavity of the low-pressure cylinder with the first opening part is formed in the first partition plate; an intermediate cavity is enclosed between the first clapboard and the inner wall of the first cavity part; or the middle cavity comprises the first cavity part, so that the first cavity part is enclosed between the first partition plate and the inner wall of the first concave cavity part.

Further, the middle cavity comprises a first cavity part and a second cavity part which are communicated with each other, and at least part of the first cavity part is enclosed by the first flange; the compressor further comprises a second partition plate arranged between the low-pressure cylinder and the high-pressure cylinder, and at least part of the second cavity part is enclosed by the second partition plate.

Further, the compressor includes: and the second partition plate is arranged between the low-pressure cylinder and the high-pressure cylinder, and at least part of the middle cavity is arranged on the second partition plate.

Further, the second partition plate is provided with a second cavity portion and a second opening portion communicating with the second cavity portion, and the compressor further includes: the third partition plate is arranged between the low-pressure cylinder and the high-pressure cylinder, and the third partition plate is arranged opposite to the second opening part so that at least part of an intermediate cavity is enclosed between the inner wall of the second cavity part and the third partition plate; and the third clapboard is provided with a second communication hole for communicating the second opening part with the cavity of the high-pressure cylinder.

According to a second aspect of the present invention, there is provided an air conditioner comprising the compressor described above.

According to a third aspect of the present invention, there is provided a water heater comprising the compressor described above.

By applying the technical scheme, the invention provides a compressor which comprises a crankshaft, a high-pressure cylinder and at least one low-pressure cylinder, wherein the crankshaft is arranged on the low-pressure cylinder and the high-pressure cylinder in a penetrating manner, and the low-pressure cylinder is positioned on one side of the high-pressure cylinder, which is close to a motor of the compressor; the compressor is provided with an intermediate cavity, and the intermediate cavity is positioned on one side of the high-pressure cylinder close to the motor, so that the refrigerant flowing out of the low-pressure cylinder flows into the high-pressure cylinder after passing through the intermediate cavity; wherein, the ratio scope of total volume V of middle chamber and total discharge capacity K of low pressure jar is: V/K is more than or equal to 1.5 and less than or equal to 5. By setting the ratio range, an intermediate cavity with reasonable volume can be designed, the problems of unsmooth exhaust of a low-pressure cylinder and difficult suction of a high-pressure cylinder caused by the fact that the intermediate cavity of the two-stage enthalpy-increasing compressor is too small in the prior art are solved, the technical problem that pressure fluctuation of refrigerant in the cylinder of the two-stage compressor is too large is effectively improved, the running performance of the compressor is more stable, and the working noise of the compressor is reduced; meanwhile, the problem that the design and the process of the middle cavity are difficult due to the fact that the middle cavity is too large is solved, the volumetric efficiency of the compressor is improved, and the technical effects that the double-stage enthalpy-increasing compressor works more efficiently and saves energy more greatly are achieved.

Drawings

The accompanying drawings, which are incorporated in and constitute a part of this application, illustrate embodiments of the invention and, together with the description, serve to explain the invention and not to limit the invention. In the drawings:

fig. 1 shows a sectional view in one direction of a pump body structure of a compressor according to a first embodiment of the present invention;

FIG. 2 shows a cross-sectional view of the pump body structure of the compressor shown in FIG. 1 in another direction;

fig. 3 shows a sectional view in one direction of a pump body structure of a compressor according to a second embodiment of the present invention;

FIG. 4 shows a cross-sectional view of the pump body structure of the compressor shown in FIG. 3 in another direction;

fig. 5 shows a sectional view in one direction of a pump body structure of a compressor according to a third embodiment of the present invention;

FIG. 6 shows a cross-sectional view of the pump body structure of the compressor shown in FIG. 5 in another direction;

fig. 7 shows a sectional view in one direction of a pump body structure of a compressor according to a fourth embodiment of the present invention;

FIG. 8 shows a cross-sectional view of the pump body structure of the compressor shown in FIG. 7 in another direction;

fig. 9 shows a sectional view in one direction of a pump body structure of a compressor according to a fifth embodiment of the present invention;

FIG. 10 shows a cross-sectional view of the pump body structure of the compressor shown in FIG. 9 in another direction;

fig. 11 is a sectional view showing a pump body structure of a compressor according to a sixth embodiment of the present invention in one direction;

FIG. 12 shows a cross-sectional view in another direction of the pump body structure of the compressor shown in FIG. 11;

fig. 13 is a sectional view showing a pump body structure of a compressor according to a seventh embodiment of the present invention;

fig. 14 is a sectional view showing a pump body structure of a compressor according to an eighth embodiment of the present invention;

fig. 15 shows a sectional view of a first flange and a first partition plate in a pump body structure of a compressor according to an embodiment of the present invention;

fig. 16 shows a sectional view of a second partition plate and a third partition plate in a pump body structure of a compressor according to an embodiment of the present invention;

fig. 17 shows a relationship between a ratio V/K between a total volume of the intermediate chamber and a total displacement of the low pressure cylinder and a ratio COP between an actual cooling capacity and a consumed power of the compressor when the compressor has a single low pressure cylinder; and

fig. 18 shows the relationship of the ratio V/K between the total volume of the intermediate chamber and the total displacement of the low pressure cylinders and the ratio COP between the actual cooling capacity and the consumed power of the compressor when the compressor has a plurality of low pressure cylinders.

Wherein the figures include the following reference numerals:

1. a crankshaft; 2. a low pressure cylinder; 201. a first low pressure cylinder; 202. a second low pressure cylinder; 3. a high pressure cylinder; 4. a middle partition plate; 5. a middle cavity; 501. a first cavity portion; 502. a second chamber portion; 6. a first flange; 601. a first cavity portion; 7. a first separator; 8. a second separator; 801. a second pocket portion; 9. a third separator; 10. a second flange; 11. a muffler; 12. an exhaust gas circulation hole; 100. and a gas supply channel.

Detailed Description

It should be noted that, in the present application, the embodiments and features of the embodiments may be combined with each other without conflict. The present invention will be described in detail below with reference to the embodiments with reference to the attached drawings.

As shown in fig. 1 to 16, the present invention provides a compressor including: a crankshaft 1; the compressor comprises a high-pressure cylinder 3 and at least one low-pressure cylinder 2, wherein a crankshaft 1 penetrates through the low-pressure cylinder 2 and the high-pressure cylinder 3, and the low-pressure cylinder 2 is positioned on one side, close to a motor of the compressor, of the high-pressure cylinder 3; the compressor is provided with an intermediate cavity 5, the intermediate cavity 5 is positioned on one side of the high-pressure cylinder 3 close to the motor, so that the refrigerant flowing out of the low-pressure cylinder 2 flows into the high-pressure cylinder 3 after passing through the intermediate cavity 5; wherein, the ratio range of the total volume V of the middle cavity 5 and the total displacement K of the low-pressure cylinder 2 is as follows: V/K is more than or equal to 1.5 and less than or equal to 5.

The invention provides a compressor, which comprises a crankshaft 1, a high-pressure cylinder 3 and at least one low-pressure cylinder 2, wherein the crankshaft 1 is arranged on the low-pressure cylinder 2 and the high-pressure cylinder 3 in a penetrating manner, and the low-pressure cylinder 2 is positioned on one side of the high-pressure cylinder 3, which is close to a motor of the compressor; the compressor is provided with an intermediate cavity 5, the intermediate cavity 5 is positioned on one side of the high-pressure cylinder 3 close to the motor, so that the refrigerant flowing out of the low-pressure cylinder 2 flows into the high-pressure cylinder 3 after passing through the intermediate cavity 5; wherein, the ratio range of the total volume V of the middle cavity 5 and the total displacement K of the low-pressure cylinder 2 is as follows: V/K is more than or equal to 1.5 and less than or equal to 5. By setting the ratio range, the intermediate cavity 5 with reasonable volume can be designed, the problems of unsmooth exhaust of a low-pressure cylinder and difficult suction of a high-pressure cylinder caused by the fact that the intermediate cavity of the double-stage enthalpy-increasing compressor is too small in the prior art are solved, the technical problem that pressure fluctuation of refrigerant in the cylinder of the double-stage compressor is too large is effectively improved, the running performance of the compressor is more stable, and the working noise of the compressor is reduced; meanwhile, the problem that the design and the process of the middle cavity are difficult due to the fact that the middle cavity is too large is solved, the volumetric efficiency of the compressor is improved, and the technical effects that the double-stage enthalpy-increasing compressor works more efficiently and saves energy more greatly are achieved.

Specifically, the volumetric efficiency of the compressor refers to a ratio of an actual cooling capacity to a theoretical cooling capacity of the compressor.

Alternatively, there is one low-pressure cylinder 2, and the ratio of the total volume V of the intermediate chamber 5 to the total displacement K of the low-pressure cylinder 2 ranges: V/K is more than or equal to 1.5 and less than or equal to 4.5; or the number of the low pressure cylinders 2 is multiple, and the low pressure cylinders 2 are sequentially arranged along the direction far away from the high pressure cylinder 3; the total displacement K of the low-pressure cylinders 2 is the sum of the displacements of the low-pressure cylinders 2, and the ratio range of the total volume V of the intermediate cavity 5 to the total displacement K of the low-pressure cylinders 2 is as follows: V/K is more than or equal to 2.0 and less than or equal to 5.0.

As shown in fig. 1 to 12, when the low pressure cylinders 2 in the compressor are single, the ratio of the total volume V of the intermediate chamber 5 to the total displacement K of the low pressure cylinders 2 ranges: V/K is more than or equal to 1.5 and less than or equal to 4.5. Therefore, two cylinders work in the compressor, which is beneficial to smooth exhaust of the low pressure cylinder 2 and stable suction of the high pressure cylinder 3, so that the compressor can stably operate, and the working noise of the compressor is effectively reduced.

The above ratio range is a better ratio range obtained through a large number of experiments and simulation processes, when the total volume V of the middle cavity 5 is set in the range, the compressor obtains a better operation effect, and in the range, the larger the value of V/K is, the higher the performance of the compressor is.

The relationship between the total volume of the intermediate cavity 5 and the total displacement of the low-pressure cylinder 2 in the compressor with two cylinders is defined through the proportional relationship and the numerical range, so that the reasonable volume of the intermediate cavity 5 is designed, the running performance of the compressor is stable, and the working noise of the compressor is reduced; meanwhile, the volume efficiency of the compressor can be effectively improved, and the high efficiency and energy conservation of the double-stage enthalpy-increasing compressor are improved.

As shown in fig. 17, there is shown a relationship between a ratio V/K of the total volume of the intermediate chamber 5 to the total displacement of the low pressure cylinders 2 and a ratio COP of the actual cooling capacity to the consumed power of the compressor (i.e., an energy efficiency ratio of the compressor) when the compressor has a single low pressure cylinder.

As shown in fig. 13 to 14, when there are two or more low pressure cylinders 2 in the compressor, the ratio of the total volume V of the intermediate chamber 5 to the total displacement K of the low pressure cylinders 2 ranges: V/K is more than or equal to 2.0 and less than or equal to 5.0. Therefore, the compressor is provided with a plurality of cylinders for working, which is beneficial to smooth exhaust of the low pressure cylinder 2 and stable suction of the high pressure cylinder 3, so that the compressor can stably run, and the working noise of the compressor is effectively reduced.

The relationship between the total volume of the intermediate chamber 5 and the total displacement of the low-pressure cylinder 2 in the compressor with a plurality of cylinders is defined through the proportional relationship and the numerical range, so that the reasonable volume of the intermediate chamber 5 is designed, the running performance of the compressor is stable, and the working noise of the compressor is reduced; meanwhile, the volume efficiency of the compressor can be effectively improved, and the high efficiency and energy conservation of the double-stage enthalpy-increasing compressor are improved.

As shown in fig. 18, there is shown a relationship between a ratio V/K of the total volume of the intermediate chamber 5 to the total displacement of the low pressure cylinders 2 and a ratio COP of the actual cooling capacity to the consumed power of the compressor (i.e., an energy efficiency ratio of the compressor) when the compressor has a plurality of low pressure cylinders.

Preferably, the low pressure cylinder 2 is one, and the intermediate chamber 5 is arranged on the side of the low pressure cylinder 2 far away from the high pressure cylinder 3; or the intermediate chamber 5 is arranged between the low pressure cylinder 2 and the high pressure cylinder 3; or the middle cavity 5 comprises a first cavity part 501 and a second cavity part 502 which are communicated with each other, the first cavity part 501 is positioned on one side of the low pressure cylinder 2 far away from the high pressure cylinder 3, and the second cavity part 502 is positioned between the low pressure cylinder 2 and the high pressure cylinder 3; the total volume V of the intermediate chamber 5 is the sum of the volumes of the first and

second chamber portions

501, 502.

As shown in fig. 15, a sectional view of the first flange and the first partition plate constituting the intermediate chamber is shown.

As shown in fig. 16, which is a sectional view of the second flange and the third partition plate constituting the middle chamber.

In fig. 1 to 14, each arrow is used to indicate the flow direction of the gas. Each embodiment has three arrows with different sizes, and the largest arrow represents low-pressure gas, namely low-temperature and low-pressure refrigerant entering the low-pressure cylinder 2 through the liquid distributor; the smallest arrow indicates high-pressure gas, namely, refrigerant compressed by the high-pressure cylinder 3; the arrow between the maximum and minimum indicates the medium pressure gas, i.e. the medium pressure refrigerant compressed by the low pressure cylinder 2.

As shown in fig. 1 to 4, in the two embodiments, the low pressure cylinder 2 in the compressor is single, the middle chamber 5 is two, the low pressure cylinder 2 is disposed on one side of the high pressure cylinder 3 close to the motor, the middle chamber 5 is divided into a first chamber portion 501 and a second chamber portion 502, the first chamber portion 501 and the second chamber portion 502 are communicated with each other and disposed on the upper and lower sides of the low pressure cylinder 2, respectively, the first chamber portion 501 is disposed above the low pressure cylinder 2, i.e., on one side of the low pressure cylinder 2 close to the motor, and the second chamber portion 502 is disposed below the low pressure cylinder 2, i.e., between the low pressure cylinder 2 and the high pressure cylinder 3. The low-pressure refrigerant is compressed by the low-pressure cylinder 2 to become medium-pressure gas, and the medium-pressure refrigerant enters the first cavity part 501 and the second cavity part 502 which are positioned above and below the low-pressure cylinder 2 from the low-pressure cylinder 2, enters the high-pressure cylinder 3 through the first cavity part 501 and the second cavity part 502, and is compressed into the high-pressure refrigerant by the high-pressure cylinder 3.

The total volume V of the intermediate chamber 5 is the first intermediate chamber volume V ₁ And a second intermediate chamber volume V ₂ Sum, i.e. V = V ₁ +V ₂ . The position relation between the first cavity part 501 and the second cavity part 502 is specifically limited through the structure, and preconditions are provided for smooth exhaust of the low pressure cylinder 2, smooth suction of the high pressure cylinder 3 and smooth running of the compressor.

As shown in fig. 5 to 8, in the two embodiments, the low pressure cylinder 2 and the intermediate chamber in the compressor are single, the low pressure cylinder 2 is disposed on the side of the high pressure cylinder 3 close to the motor, and the intermediate chamber 5 is disposed above the low pressure cylinder 2, that is, on the side of the low pressure cylinder 2 close to the motor. The low-pressure refrigerant is compressed by the low-pressure cylinder 2 to become a medium-pressure refrigerant, the medium-pressure refrigerant enters the middle cavity 5 above the low-pressure cylinder 2 from the low-pressure cylinder 2, enters the high-pressure cylinder 3 through the middle cavity 5, and is compressed into the high-pressure refrigerant by the high-pressure cylinder 3.

In the two embodiments shown in fig. 9 to 12, the low pressure cylinder 2 and the middle chamber in the compressor are single, the low pressure cylinder 2 is disposed on the side of the high pressure cylinder 3 close to the motor, and the middle chamber 5 is disposed below the low pressure cylinder 2, i.e., between the low pressure cylinder 2 and the high pressure cylinder 3, so as to reduce the flow path of the middle pressure refrigerant. The low-pressure refrigerant is compressed by the low-pressure cylinder 2 to become a medium-pressure refrigerant, the medium-pressure refrigerant enters the middle cavity 5 positioned below the low-pressure cylinder 2 from the low-pressure cylinder 2, enters the high-pressure cylinder 3 through the middle cavity 5, and is compressed into the high-pressure refrigerant by the high-pressure cylinder 3.

Preferably, the low pressure cylinder 2 is plural, and the plural low pressure cylinders 2 are arranged in sequence in a direction away from the high pressure cylinder 3; the total displacement K of the low-pressure cylinders 2 is the sum of the displacements of the low-pressure cylinders 2; the intermediate chamber 5 includes a first chamber portion 501 and a second chamber portion 502 that are communicated with each other, the first chamber portion 501 is located between the motor and the low pressure cylinder 2 of the plurality of low pressure cylinders 2 that is close to the motor, the second chamber portion 502 is located between the high pressure cylinder 3 and the low pressure cylinder 2 of the plurality of low pressure cylinders 2 that is close to the high pressure cylinder 3, and a total volume V of the intermediate chamber 5 is a sum of volumes of the first chamber portion 501 and the second chamber portion 502, that is, V = V ₁ +V ₂ 。

As shown in fig. 13 and 14, in the two embodiments, the number of the low pressure cylinders 2 in the compressor is plural, the number of the intermediate chambers is two, each of the low pressure cylinders 2 is sequentially arranged on one side of the high pressure cylinder 3 close to the motor along the direction of the axis of the crankshaft 1, the intermediate chamber 5 is divided into a first chamber portion 501 and a second chamber portion 502, the first chamber portion 501 and the second chamber portion 502 are communicated with each other, the first chamber portion 501 is arranged above the low pressure cylinder 2 close to the motor, that is, on one side of the first low pressure cylinder 201 close to the motor, and the second chamber portion 502 is arranged below the low pressure cylinder 2 close to the high pressure cylinder 3, that is, between the second low pressure cylinder 202 and the high pressure cylinder 3. The low-pressure refrigerant is compressed by the two low-pressure cylinders 2 to become a medium-pressure refrigerant, the medium-pressure refrigerant correspondingly enters the first cavity portion 501 and the second cavity portion 502 which are positioned above and below the medium-pressure refrigerant from the low-pressure cylinders 2, enters the high-pressure cylinders 3 through the first cavity portion 501 and the second cavity portion 502, and is compressed into the high-pressure refrigerant through the high-pressure cylinders 3.

Specifically, along the axis direction of bent axle 1, a plurality of low pressure jar 2 overlap in proper order and establish on the corresponding shaft section of bent axle 1, are provided with intermediate bottom 4 between two adjacent low pressure jar 2, are provided with the middle intercommunicating pore that is used for communicateing the cavity of two corresponding low pressure jar 2 on intermediate bottom 4.

Optionally, the compressor comprises a gas make-up passage 100, the gas make-up passage 100 being arranged on one of the at least one low-pressure cylinder 2; or the compressor comprises a plurality of air replenishing channels 100, the number of the low pressure cylinders 2 is multiple, and the plurality of air replenishing channels 100 are arranged on the plurality of low pressure cylinders 2 in a one-to-one correspondence manner.

As shown in the embodiments of fig. 1 to 12, the compressor of these embodiments has a single low pressure cylinder 2 and has a charge air passage 100, and this charge air passage 100 is provided on the low pressure cylinder 2. The arrangement can increase the discharge capacity of the low-pressure cylinder 2 in the compressor, improve the refrigerating capacity of the compressor under working conditions such as low temperature and the like, improve the continuity of air suction and exhaust of the low-pressure cylinder 2 in the compressor, and improve the airflow noise and the integral vibration of the compressor.

As shown in fig. 13, the compressor of the present embodiment has two low pressure cylinders 2, and has an air supply passage 100, and the air supply passage 100 is provided in the low pressure cylinder 2 away from the high pressure cylinder 3. The arrangement can increase the discharge capacity of the low-pressure cylinder 2 in the compressor, improve the refrigerating capacity of the compressor under working conditions such as low temperature and the like, improve the continuity of air suction and exhaust of the low-pressure cylinder 2 in the compressor, and improve the airflow noise and the integral vibration of the compressor.

As shown in the embodiment of fig. 14, the compressor in this embodiment has two compressors 2 with low pressure cylinders, and has two air supply passages 100, and the two air supply passages 100 are respectively disposed on the two low pressure cylinders 2. In this way, it is ensured that the exhaust gases of the low pressure cylinder 2 are sufficiently mixed with the system charge air in the intermediate chamber 5. The arrangement can increase the displacement of the low-pressure cylinder 2 in the compressor, improve the refrigerating capacity of the compressor under the working conditions of low temperature and the like, improve the continuity of air suction and exhaust of the low-pressure cylinder 2 in the compressor, and improve the air flow noise and the integral vibration of the compressor.

As shown in fig. 1 to 8, the compressor further includes: a first flange 6, the first flange 6 being arranged on the side of the low pressure cylinder 2 close to the electric machine, at least part of the intermediate chamber 5 being arranged on the first flange 6. I.e. a first flange 6, is located above the low pressure cylinder 2 for enclosing an intermediate chamber 5 located above the low pressure cylinder 2.

As shown in fig. 1 to 8, the first flange 6 has a first cavity 601 and a first opening portion communicating with the first cavity 601, the first opening portion being provided toward the low pressure cylinder 2; the first cavity portion 601 is for forming the intermediate cavity 5. I.e. the first cavity part 601 of the first flange 6, is used to constitute the intermediate chamber 5 above the low pressure cylinder 2.

As shown in fig. 1 to 8, the compressor further includes a first partition plate 7, the first partition plate 7 is disposed opposite to the first opening, and the first partition plate 7 is provided with a first communication hole for communicating the cavity of the low pressure cylinder 2 with the first opening; an intermediate cavity 5 is enclosed between the first clapboard 7 and the inner wall of the first cavity part 601; or the intermediate chamber 5 includes the first chamber portion 501 so that the first chamber portion 501 is enclosed between the first partition 7 and the inner wall of the first cavity portion 601.

Specifically, the first partition 7 is disposed on one side of the first opening of the first flange 6, and the first partition 7 is attached to an end surface of the first flange 6 on one side of the first opening to close the first opening, so that the intermediate chamber 5 or the first chamber portion 501 located above the low pressure cylinder 2 is enclosed between the first partition 7 and the inner wall of the first cavity portion 601. In addition, the first partition 7 is further provided with a first communication hole, which is used for communicating the cavity of the low pressure cylinder 2 with the intermediate cavity 5 or the first cavity portion 501, so that the compressed medium pressure refrigerant in the cavity of the low pressure cylinder 2 can enter the intermediate cavity 5 or the first cavity portion 501 through the first communication hole.

In both embodiments shown in fig. 5 to 8, the low pressure cylinder 2 and the intermediate chamber in the compressor are single, and the intermediate chamber 5 located above the low pressure cylinder 2 is enclosed between the first partition 7 and the inner wall of the first chamber portion 601.

In the two embodiments shown in fig. 1 to 4, the low pressure cylinder 2 in the compressor is single and the intermediate chamber is two, and the first partition 7 and the inner wall of the first cavity 601 enclose the first cavity 501 of the intermediate chamber 5 above the low pressure cylinder 2.

As shown in fig. 1 to 4, the intermediate chamber 5 includes a first chamber portion 501 and a second chamber portion 502 which are communicated with each other, at least a part of the first chamber portion 501 is surrounded by a first flange 6; the compressor further comprises a second partition 8, the second partition 8 being arranged between the low pressure cylinder 2 and the high pressure cylinder 3, at least part of the second chamber portion 502 being enclosed by the second partition 8. I.e. the second partition 8 is located below the low pressure cylinder 2 for enclosing a second chamber portion 502 located below the low pressure cylinder 2.

As shown in fig. 1 to 4 and 9 to 12, the compressor includes: a second diaphragm 8, the second diaphragm 8 being arranged between the low pressure cylinder 2 and the high pressure cylinder 3, at least part of the intermediate chamber 5 being arranged on the second diaphragm 8. I.e. the second partition 8 is located below the low pressure cylinder 2 and above the high pressure cylinder 3 for enclosing the intermediate chamber 5 located below the low pressure cylinder 2.

Specifically, the second partition plate 8 is provided with a second cavity portion 801 and a second opening portion communicating with the second cavity portion 801, and the compressor further includes: a third partition plate 9, the third partition plate 9 being provided between the low pressure cylinder 2 and the high pressure cylinder 3, the third partition plate 9 being provided so as to face the second opening portion, so that at least a part of the intermediate chamber 5 is enclosed between the inner wall of the second cavity portion 801 and the third partition plate 9; wherein, the third partition 9 is provided with a second communication hole for communicating the second opening portion with the chamber of the high pressure cylinder 3.

The third partition 9 is located between the low pressure cylinder 2 and the high pressure cylinder 3, the third partition 9 is disposed at a side close to the second opening of the second partition 8, and the third partition 9 is attached to an end face of the second partition 8 located at the side of the second opening to close the second opening, so that the intermediate chamber 5 located below the low pressure cylinder 2 is enclosed between the third partition 9 and an inner wall of the second cavity portion 801. In addition, the third partition 9 is further provided with a third communication hole for communicating the cavity of the high pressure cylinder 3 with the intermediate chamber 5, so that the medium pressure refrigerant in the intermediate chamber 5 can enter the cavity of the high pressure cylinder 3 through the third communication hole.

In the two embodiments shown in fig. 9 to 12, the low pressure cylinder 2 and the intermediate chamber in the compressor are single, and the intermediate chamber 5 located below the low pressure cylinder 2 is enclosed between the third partition 9 and the inner wall of the second cavity portion 801.

In the two embodiments shown in fig. 1 to 4, the low pressure cylinder 2 in the compressor is single and the intermediate chamber is two, and the second chamber portion 502 of the intermediate chamber 5 located below the low pressure cylinder 2 is enclosed between the third partition 9 and the inner wall of the second chamber portion 801.

Specifically, the second diaphragm 8 is located on the side of the third diaphragm 9 close to the low pressure cylinder 2. I.e. the third partition 9 is located between the second partition 8 and the high-pressure cylinder 3.

The second opening of the second partition 8 faces the direction toward the high pressure cylinder 3, and the second partition 8 is provided with a second communication hole for communicating the chamber of the low pressure cylinder 2 with the intermediate chamber 5, so that the intermediate pressure gas in the low pressure cylinder 2 can enter the intermediate chamber 5 through the second communication hole.

In the embodiment in which the intermediate chamber 5 or the first chamber portion 501 is provided on the side of the low pressure cylinder 2 remote from the high pressure cylinder 3, in order to allow the intermediate pressure gas in the intermediate chamber 5 or the first chamber portion 501 located above the low pressure cylinder 2 to enter the high pressure cylinder 3, an intermediate chamber communication hole is provided in the low pressure cylinder 2, and a hole capable of communicating with the intermediate chamber communication hole is provided in the first partition plate 7 so that the intermediate pressure gas in the intermediate chamber 5 located above the low pressure cylinder 2 can flow below the low pressure cylinder 2.

When the low pressure cylinder 2 in the compressor is single and the intermediate chamber is two, the upper and lower sides of the low pressure cylinder 2 are respectively provided with the first chamber portion 501 and the second chamber portion 502, and a hole communicated with the intermediate chamber communication hole also needs to be formed in the second partition plate 8 on the side of the second chamber portion 502 close to the low pressure cylinder 2, so that the first chamber portion 501 and the second chamber portion 502 are communicated.

In the embodiment where the intermediate chamber 5 is provided with only one hole and is disposed on the side of the low pressure cylinder 2 away from the high pressure cylinder 3, a third partition plate 9 is disposed between the low pressure cylinder 2 and the high pressure cylinder 3, and a hole communicating with the intermediate chamber communication hole is also required to be disposed in the third partition plate 9, so that the gas in the intermediate chamber 5 can enter the high pressure cylinder 3 through the holes communicating with the first partition plate 7, the low pressure cylinder 2, and the third partition plate 9.

As shown in fig. 1 to 14, the compressor further includes: the silencer 11, the silencer 11 is located the high pressure cylinder 3 and keeps away from one side of low pressure cylinder 2, and the silencer 11 has the amortization chamber, and the amortization chamber is connected with the piston chamber of high pressure cylinder 3 to make the refrigerant that flows out by high pressure cylinder 3 flow into the amortization intracavity. Thus, the high-pressure gas compressed by the high-pressure cylinder 3 enters the silencing cavity of the silencer 11, so that the noise generated by the pump body structure is reduced by the silencer 11.

The compressor further includes: and the second flange 10 are positioned between the high-pressure cylinder 3 and the silencer 11 so as to seal the silencing cavity, so that the second flange 10 and the silencer 11 jointly form a high-pressure exhaust cavity, and the second flange 10 is provided with a fourth communication hole for communicating the silencing cavity with the cavity of the high-pressure cylinder 3, so that the refrigerant flowing out of the high-pressure cylinder 3 flows into the silencing cavity through the fourth communication hole.

Specifically, the compressor has an exhaust flow through hole 12 communicating with the sound deadening chamber, and the exhaust flow through hole 12 communicates with the sound deadening chamber and penetrates the first flange 6, the first partition plate 7, the low pressure cylinder 2, the second partition plate 8, the third partition plate 9, and the high pressure cylinder 3.

An exhaust through hole 12 is arranged in the pump body structure of the compressor, the exhaust through hole 12 penetrates through the whole pump body structure, and the position of the exhaust through hole 12 is close to the exhaust side of the pump body structure. After the high pressure cylinder 3 is compressed, the high pressure gas enters the muffler 11 through the exhaust port of the second flange 10, and the high pressure gas in the muffler 11 enters the shell space of the compressor through the exhaust gas flowing hole 12.

In the embodiments of the present invention, the first flange 6, the first partition 7, the low pressure cylinder 2, the second partition 8, the third partition 9, the high pressure cylinder 3, and the second flange 10 are all provided with high pressure flow holes, which make the high pressure flow holes in a mutually communicated state when they are assembled, and these communicated high pressure flow holes jointly constitute the exhaust flow through hole 12 of the pump body structure, so that the high pressure gas in the muffler 11 can be discharged to the outside of the pump body structure through these communicated high pressure flow holes (i.e., the exhaust flow through hole 12).

Optionally, the compressor further comprises a first flange 6, and the first flange 6 is positioned on one side of the low pressure cylinder 2 close to the motor; wherein the first flange 6 and/or the low pressure cylinder 2 is/are fixedly connected with the shell of the compressor.

In the first, third, fifth, seventh and eighth embodiments shown in fig. 1 to 2, 5 and 6, 9 and 10, 13 and 14, the casing of the compressor fixes the pump body structure by welding with the low pressure cylinder 2.

In the second, fourth and sixth embodiments shown in fig. 3 and 4, and in fig. 7 and 8, and in fig. 11 and 12, the casing of the compressor fixes the pump body structure by welding to the first flange 6.

The invention provides an air conditioner which comprises the compressor. The air conditioner of the invention improves the running performance of the air conditioner by using the compressor.

The invention provides a water heater which comprises the compressor. The water heater is a heat pump water heater, and the running performance of the heat pump water heater is improved by using the compressor.

From the above description, it can be seen that the above-described embodiments of the present invention achieve the following technical effects:

the compressor comprises a crankshaft 1, a high-pressure cylinder 3 and at least one low-pressure cylinder 2, wherein the crankshaft 1 is arranged on the low-pressure cylinder 2 and the high-pressure cylinder 3 in a penetrating mode, and the low-pressure cylinder 2 is located on one side, close to a motor of the compressor, of the high-pressure cylinder 3; the compressor is provided with an intermediate cavity 5, the intermediate cavity 5 is positioned on one side of the high-pressure cylinder 3 close to the motor, so that the refrigerant flowing out of the low-pressure cylinder 2 flows into the high-pressure cylinder 3 after passing through the intermediate cavity 5; wherein, the ratio range of the total volume V of the middle cavity 5 and the total displacement K of the low-pressure cylinder 2 is as follows: V/K is more than or equal to 1.5 and less than or equal to 5.

By setting the ratio range, the middle cavity 5 with reasonable volume can be designed, the technical effects of smooth exhaust of the low pressure cylinder and stable suction of the high pressure cylinder of the two-stage enthalpy-increasing compressor when the low pressure cylinder 2 is single-cylinder or multi-cylinder are realized, the technical problem of overlarge pressure fluctuation of a refrigerant in the cylinder of the two-stage compressor is effectively improved, the running performance of the compressor is more stable, and the working noise of the compressor is reduced; meanwhile, the problem that the design and the process of the middle cavity are difficult due to the fact that the middle cavity is too large is solved, the volumetric efficiency of the compressor is improved, and the technical effects that the double-stage enthalpy-increasing compressor works more efficiently and saves energy more greatly are achieved.

The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. A compressor, comprising:

a crankshaft (1);

the compressor comprises a high-pressure cylinder (3) and at least one low-pressure cylinder (2), wherein a crankshaft (1) penetrates through the low-pressure cylinder (2) and the high-pressure cylinder (3), and the low-pressure cylinder (2) is located on one side, close to a motor of the compressor, of the high-pressure cylinder (3);

the compressor is provided with an intermediate cavity (5), and the intermediate cavity (5) is positioned on one side of the high-pressure cylinder (3) close to the motor, so that the refrigerant flowing out of the low-pressure cylinder (2) flows into the high-pressure cylinder (3) after passing through the intermediate cavity (5);

wherein, the ratio range of the total volume V of the middle cavity (5) and the total displacement K of the low pressure cylinder (2) is as follows: V/K is more than or equal to 1.5 and less than or equal to 5;

the low-pressure cylinder (2) is one, and the range of the ratio of the total volume V of the middle cavity (5) to the total displacement K of the low-pressure cylinder (2) is as follows: V/K is more than or equal to 1.5 and less than or equal to 4.5; or alternatively

The number of the low-pressure cylinders (2) is multiple, and the low-pressure cylinders (2) are sequentially arranged along the direction far away from the high-pressure cylinder (3); the total displacement K of the low pressure cylinders (2) is the sum of the displacements of the low pressure cylinders (2), and the ratio range of the total volume V of the intermediate cavity (5) to the total displacement K of the low pressure cylinders (2) is as follows: V/K is more than or equal to 2.0 and less than or equal to 5.0.

2. Compressor, according to claim 1, characterized in that said low pressure cylinder (2) is one,

the middle cavity (5) is arranged on one side of the low-pressure cylinder (2) far away from the high-pressure cylinder (3); or

The intermediate chamber (5) is arranged between the low pressure cylinder (2) and the high pressure cylinder (3); or

The middle cavity (5) comprises a first cavity part (501) and a second cavity part (502) which are communicated with each other, the first cavity part (501) is positioned on one side of the low-pressure cylinder (2) far away from the high-pressure cylinder (3), and the second cavity part (502) is positioned between the low-pressure cylinder (2) and the high-pressure cylinder (3); the total volume V of the intermediate chamber (5) is the sum of the volumes of the first and second chamber portions (501, 502).

3. Compressor according to claim 1, characterized in that said low pressure cylinder (2) is a plurality of said low pressure cylinders (2) arranged one after the other in a direction away from said high pressure cylinder (3); the total displacement K of the low-pressure cylinders (2) is the sum of the displacements of the low-pressure cylinders (2);

the middle cavity (5) comprises a first cavity portion (501) and a second cavity portion (502) which are communicated with each other, the first cavity portion (501) is located on one side, away from the high-pressure cylinder (3), of the low-pressure cylinders (2) close to the motor, of the low-pressure cylinders (2), the second cavity portion (502) is located between the low-pressure cylinder (2) and the high-pressure cylinder (3), close to the high-pressure cylinder (3), of the low-pressure cylinders (2), and the total volume V of the middle cavity (5) is the sum of the volumes of the first cavity portion (501) and the second cavity portion (502).

4. The compressor according to claim 3, wherein along the axial direction of the crankshaft (1), a plurality of the low pressure cylinders (2) are sequentially sleeved on the corresponding shaft sections of the crankshaft (1), a middle partition plate (4) is arranged between every two adjacent low pressure cylinders (2), and a middle communication hole for communicating the cavities of the corresponding two low pressure cylinders (2) is arranged on the middle partition plate (4).

5. Compressor in accordance with claim 1,

the compressor comprises an air supply channel (100), wherein the air supply channel (100) is arranged on one low-pressure cylinder (2) of the at least one low-pressure cylinder (2); or

The compressor comprises a plurality of air replenishing channels (100), the low-pressure cylinders (2) are multiple, and the air replenishing channels (100) are arranged on the low-pressure cylinders (2) in a one-to-one correspondence mode.

6. The compressor of claim 1, further comprising:

a first flange (6), the first flange (6) is arranged on one side of the low pressure cylinder (2) close to the motor, and at least part of the middle cavity (5) is arranged on the first flange (6).

7. The compressor according to claim 6, wherein the first flange (6) has a first cavity portion (601) and a first opening portion communicating with the first cavity portion (601), the first opening portion being provided toward the low pressure cylinder (2); the first cavity part (601) is used for forming the intermediate cavity (5).

8. The compressor according to claim 7, further comprising a first partition plate (7), wherein the first partition plate (7) is disposed opposite to the first opening portion, and a first communication hole for communicating the cavity of the low pressure cylinder (2) and the first opening portion is disposed on the first partition plate (7);

the first clapboard (7) and the inner wall of the first cavity part (601) enclose the middle cavity (5); or alternatively

The intermediate cavity (5) comprises a first cavity part (501) so that the first cavity part (501) is enclosed between the first partition plate (7) and the inner wall of the first cavity part (601).

9. Compressor according to claim 6, characterized in that said intermediate chamber (5) comprises a first chamber portion (501) and a second chamber portion (502) communicating with each other, at least part of said first chamber portion (501) being surrounded by said first flange (6); the compressor further comprises a second partition (8), the second partition (8) being arranged between the low pressure cylinder (2) and the high pressure cylinder (3), at least part of the second chamber portion (502) being enclosed by the second partition (8).

10. The compressor of claim 1, comprising:

a second partition (8), said second partition (8) being arranged between said low pressure cylinder (2) and said high pressure cylinder (3), at least part of said intermediate chamber (5) being arranged on said second partition (8).

11. The compressor according to claim 10, wherein a second cavity portion (801) and a second opening portion communicating with the second cavity portion (801) are provided in the second partition plate (8), and the compressor further comprises:

a third partition plate (9), the third partition plate (9) being disposed between the low pressure cylinder (2) and the high pressure cylinder (3), the third partition plate (9) being disposed opposite to the second opening portion such that at least a part of the intermediate chamber (5) is enclosed between an inner wall of the second cavity portion (801) and the third partition plate (9);

and a second communication hole for communicating the second opening part and the cavity of the high-pressure cylinder (3) is formed in the third partition plate (9).

12. An air conditioner characterized by comprising the compressor of any one of claims 1 to 11.

13. A water heater comprising a compressor as claimed in any one of claims 1 to 11.