CN111594442B

CN111594442B - Compressor assembly, air conditioning system and control method of air conditioning system

Info

Publication number: CN111594442B
Application number: CN202010399700.8A
Authority: CN
Inventors: 李健; 霍喜军
Original assignee: Gree Electric Appliances Inc of Zhuhai; Zhuhai Landa Compressor Co Ltd
Current assignee: Gree Electric Appliances Inc of Zhuhai; Zhuhai Landa Compressor Co Ltd
Priority date: 2020-05-12
Filing date: 2020-05-12
Publication date: 2024-05-14
Anticipated expiration: 2040-05-12
Also published as: CN111594442A

Abstract

The invention provides a compressor assembly, an air conditioning system and a control method thereof, wherein the compressor assembly comprises: the compressor is provided with in the casing of compressor: the exhaust cavity is formed on the shell, and a main exhaust port communicated with the exhaust cavity is formed on the shell; the parallel exhaust port of the parallel cylinder is provided with a parallel exhaust control valve and a parallel heat return pipe, and the parallel heat return pipe is connected with the parallel exhaust control valve and the exhaust cavity; the first exhaust port of the first variable volume cylinder is provided with a first control valve and a first heat return pipe, and the first heat return pipe is connected with the first control valve and the exhaust cavity; the second exhaust port of the second variable volume cylinder is provided with a second control valve and a second heat return pipe, and the second heat return pipe is connected with the second control valve and the exhaust cavity. The invention makes the compressor more stable, the running mode is diversified, the energy efficiency is higher.

Description

Compressor assembly, air conditioning system and control method of air conditioning system

Technical Field

The present invention relates to the field of compressors, and in particular, to a compressor assembly, an air conditioning system, and a control method thereof.

Background

The existing three-cylinder compressor is of a one-cylinder variable capacity and two-stage enthalpy-increasing structure, and the structure is characterized in that a variable capacity cylinder is newly added on the basis of a double-cylinder compressor of the two-stage enthalpy-increasing structure, so that the functions of double cylinders and three cylinders (the single cylinder cannot be realized), the cost of the compressor is high, the problem of serious vibration is solved, and when the compressor is operated at low temperature and low frequency, APF (intermediate refrigeration) is not high enough and the heating performance is poor because the low-load performance advantage is not great; in addition, when the compressor and the air conditioning system are operated, the cooling, refrigerating and dehumidifying are completed in one system, so that the heat exchange efficiency of the evaporator is low, the air conditioning system cannot meet the refrigerating, dehumidifying and heating requirements of the north region of the Yangtze river basin, and serious hidden hazards are caused to the energy efficiency and after-sale experience of the air conditioning system.

Different air cylinders of the existing three-cylinder compressor exhaust gas enters the exhaust cavity after passing through the driving motor and other structures on the upper portion of the compressor, so that the flow resistance and the pressure pulsation of the exhaust gas are large, the running noise and the vibration of the compressor are obvious, the compressor is low in energy, the comfort level of customer experience is poor, and the product preempting market is not provided with any advantage.

Disclosure of Invention

In view of the above, the present invention provides a compressor assembly, an air conditioning system and a control method thereof, so as to solve the technical problems of single operation mode and low energy efficiency of the compressor in the prior art, and in particular:

in a first aspect, the present invention provides a compressor assembly comprising: the compressor, be provided with in the casing of compressor:

the shell is provided with a main exhaust port communicated with the exhaust cavity;

the parallel exhaust port of the parallel cylinder is provided with a parallel exhaust control valve and a parallel heat return pipe, the parallel heat return pipe is connected with the parallel exhaust control valve and the exhaust cavity, and the parallel exhaust control valve is used for enabling the parallel exhaust port to be communicated with the exhaust cavity or enabling the parallel exhaust port to be communicated with the outside of the shell;

The first exhaust port of the first variable volume cylinder is provided with a first control valve and a first heat return pipe, the first heat return pipe is connected with the first control valve and the exhaust cavity, and the first control valve is used for enabling the first exhaust port to be communicated with the exhaust cavity or enabling the first exhaust port to be communicated with the outside of the shell;

The second control valve is used for communicating the second exhaust port with the exhaust cavity or communicating the second exhaust port with the outside of the shell.

Further optionally, the cylinder volume of the parallel cylinder is smaller than the cylinder volume of the first variable-volume cylinder, and the cylinder volume of the first variable-volume cylinder is smaller than the cylinder volume of the second variable-volume cylinder.

Further alternatively, the cylinder volume ratio of the parallel cylinder to the first variable-volume cylinder is 0.08-0.6.

Further alternatively, the cylinder volume ratio of the first and second varactors is 0.4-0.9.

Further alternatively, the cylinder volume ratio of the parallel cylinder to the second variable-volume cylinder is 0.15-0.85.

Further alternatively, the end parts of the parallel cylinder and the second variable volume cylinder are respectively provided with an upper flange and a lower flange, a baffle plate is arranged between the variable volume cylinder and the first variable volume cylinder,

The parallel exhaust ports are arranged on the upper flange, the first exhaust ports are arranged on the partition plate, and the second exhaust ports are arranged on the lower flange.

Further alternatively, the method may comprise, in a further alternative,

A communication pipeline is arranged between a main exhaust port of the exhaust cavity and an air suction port of the parallel cylinder, and a parallel variable-volume liquid separator and a parallel variable-volume control valve are arranged on the communication pipeline;

A communication pipeline is arranged between a main exhaust port of the exhaust cavity and an air suction port of the first variable-volume cylinder, and a first variable-volume liquid separator and a first variable-volume control valve are arranged on the communication pipeline;

and a communication pipeline is arranged between the main exhaust port of the exhaust cavity and the air suction port of the second variable-volume cylinder, and a parallel variable-volume liquid separator and a second variable-volume control valve are arranged on the communication pipeline.

Further optionally, the air suction port of the parallel air cylinder is also communicated with a parallel liquid distributor;

The air suction port of the first variable-volume cylinder is also communicated with the first liquid distributor;

The air suction port of the second variable volume cylinder is also communicated with the second liquid distributor.

In a second aspect, the present invention provides an air conditioning system comprising a first heat exchange portion, a second heat exchange portion, a reversing valve, a flash evaporator and the compressor assembly described above,

The compressor component, the first heat exchange part and the second heat exchange part are sequentially connected to form a refrigerant loop,

Wherein the first port of the flash evaporator is connected with the second end of the first heat exchange part, the second port of the flash evaporator is communicated with the air suction port of the parallel cylinder, the third port of the flash evaporator is connected with the first end of the second heat exchange part,

A first flash control valve is arranged between a first port of the flash evaporator and a second end of the first heat exchange part, and a second flash control valve is arranged between a second port of the flash evaporator and an air suction port of the parallel air cylinder.

Further optionally, a reversing valve is also included,

The parallel exhaust port, the first exhaust port and the second exhaust port are simultaneously connected to one port of the reversing valve, the main exhaust port is connected to the other port of the reversing valve,

Wherein the parallel exhaust control valve comprises a second electromagnetic valve arranged between the parallel exhaust port and the reversing valve,

The first control valve comprises a fourth electromagnetic valve arranged between the first exhaust port and the reversing valve,

The second control valve comprises a sixth electromagnetic valve arranged between the second exhaust port and the reversing valve.

Further alternatively, the first heat exchange part comprises four heat exchangers arranged in parallel, the second heat exchange part comprises four heat exchangers arranged in parallel, each heat exchanger is provided with a solenoid valve at a first end,

The reversing valve comprises two four-way reversing valves which are arranged in series.

In a third aspect, there is provided a control method of the above air conditioning system, wherein the compressor assembly is provided with the following operation modes according to different operation loads of the air conditioning system:

Single cylinder mode: any one of the parallel cylinder, the first variable-volume cylinder and the second variable-volume cylinder operates, and the other two are unloaded;

Double-cylinder single-row mode: any two of the parallel cylinder, the first variable-volume cylinder and the second variable-volume cylinder operate, and the other one is unloaded and exhausted through the main exhaust port;

Double-cylinder double-row mode: any two of the parallel air cylinders, the first variable volume air cylinder and the second variable volume air cylinder operate, the other one is unloaded, and at least one operating air cylinder directly exhausts air;

three-cylinder single-row mode: the parallel cylinder, the first variable volume cylinder and the second variable volume cylinder operate simultaneously and exhaust through the main exhaust port;

Three-cylinder double-row mode: the parallel cylinders, the first variable-volume cylinder and the second variable-volume cylinder operate simultaneously, one cylinder is independently exhausted, and the other two cylinders are exhausted through the main exhaust port; three-cylinder three-row mode: and the parallel cylinder, the first variable volume cylinder and the second variable volume cylinder operate simultaneously, and at least two operating cylinders directly exhaust.

The invention is provided with three independent variable-volume cylinders, and the three cylinders are all provided with exhaust ports capable of independently exhausting, so that the compressor has a plurality of different exhaust modes so as to meet the requirements of different working modes.

Drawings

The above and other objects, features and advantages of the present disclosure will become more apparent by describing in detail exemplary embodiments thereof with reference to the attached drawings. The drawings described below are merely examples of the present disclosure and other drawings may be obtained from these drawings without inventive effort for a person of ordinary skill in the art.

FIG. 1 shows a schematic diagram of a three-cylinder pump in one embodiment;

FIG. 2 illustrates a schematic diagram of an air conditioning system in one embodiment.

In the figure:

10-a main exhaust port; 1-parallel air cylinders; 11-parallel exhaust ports; 111-a first solenoid valve; 112-a second solenoid valve; 12-a parallel knockout; 13-a parallel variable-volume knockout; 131-parallel variable capacity control valve; 132-a seventh solenoid valve; 2-a first variable volume cylinder; 21-a first exhaust port; 211-a third solenoid valve; 212-a fourth solenoid valve; 22-a first knockout; 23-a first variable volume dispenser; 231-a first variable volume control valve; 232-eighth solenoid valve; 3-a second variable volume cylinder; 31-a second exhaust port; 311-a fifth solenoid valve; 312-sixth solenoid valve; 32-a second knockout; 33-a second variable volume dispenser; 331-a third variable volume control valve; 332-a ninth solenoid valve; 4-reversing valve; 51-a first heat exchanger; 511-a first heat exchange solenoid valve; 52-a second heat exchanger; 521-a second heat exchange electromagnetic valve; 53-a third heat exchanger; 531-a third heat exchange electromagnetic valve; 54-fourth heat exchanger; 541-a fourth heat exchange solenoid valve; 6-flash evaporator; 61-a first flash control valve; 62-a second flash control valve; 71-a fifth heat exchanger; 711-a fifth heat exchange electromagnetic valve; 72-sixth heat exchanger; 721-sixth heat exchange solenoid valve; 73-seventh heat exchanger; 731-seventh heat exchange solenoid valve; 74-eighth heat exchanger; 741-eighth heat exchange solenoid valve; 8-tenth solenoid valve.

Detailed Description

For the purpose of making the objects, technical solutions and advantages of the embodiments of the present invention more apparent, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention, and it is apparent that the described embodiments are some embodiments of the present invention, but not all embodiments of the present invention. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.

The terminology used in the embodiments of the invention is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. As used in this application and the appended claims, the singular forms "a," "an," and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise, the "plurality" generally includes at least two, but does not exclude the case of at least one.

It should be understood that the term "and/or" as used herein is merely one relationship describing the association of the associated objects, meaning that there may be three relationships, e.g., a and/or B, may represent: a exists alone, A and B exist together, and B exists alone. In addition, the character "/" herein generally indicates that the front and rear associated objects are an "or" relationship.

It should also be noted that the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a product or system that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such product or system. Without further limitation, an element defined by the phrase "comprising one … …" does not exclude the presence of other like elements in a commodity or system comprising such elements.

According to the invention, three independent parallel variable-capacity cylinders are arranged to realize independent variable-capacity compression and air supplement, and good heating performance is obtained by setting the volume ratio of the three cylinders. In addition, as the sizes of the three cylinders are different, each cylinder can be independently exhausted, various different operation modes can be realized, the heating performance at the temperature of minus 15 ℃ can be effectively improved during dehumidification and heating, and the problems of vibration and the like of the compressor can be solved while the efficiency is improved. The invention is described in detail below with reference to specific examples:

Example 1

In this embodiment, the present invention provides a compressor assembly, including a housing, a cavity is formed in the housing, an exhaust chamber is formed at an upper portion of the cavity, a motor is disposed at a lower side of the exhaust chamber, three cylinders of parallel cylinders 1, a first variable-volume cylinder 2 and a second variable-volume cylinder 3 having different cylinder volumes are disposed at a lower side of the motor, the three cylinders are arranged in an uppermost side from top to bottom in an arrangement order of the parallel cylinders 1, the first variable-volume cylinder 2 is disposed at a lower side of the parallel cylinders 1, a partition plate is disposed between the two, preferably two partition plates are disposed, the second variable-volume cylinder 3 is disposed at a lower side of the first variable-volume cylinder 2, and a partition plate is disposed between the two, preferably two partition plates are disposed. The end parts of the parallel cylinder 1 and the second variable capacity cylinder 3 are respectively provided with an upper flange and a lower flange, the parallel exhaust port 11 is arranged on the upper flange, the first exhaust port 21 is arranged on the partition plate, and the second exhaust port 31 is arranged on the lower flange.

The shell is provided with a main exhaust port 10 communicated with the exhaust cavity, a parallel exhaust port 11 (namely, the exhaust port of the parallel cylinder) of the parallel cylinder 1 is communicated with the exhaust cavity through a parallel heat return pipe, and meanwhile, the parallel exhaust port 11 can directly exhaust, namely, the parallel exhaust port 11 is simultaneously connected with the parallel heat return pipe and an exhaust pipe for directly exhausting, so that the parallel cylinder 1 can exhaust gas into the exhaust cavity and can directly exhaust. A parallel exhaust control valve is provided at the parallel exhaust port 11 for controlling the parallel exhaust port 11 to communicate with the exhaust chamber or to exhaust independently. Preferably, the parallel exhaust control valve includes a first solenoid valve 111 disposed on the parallel heat return pipe, and a second solenoid valve 112 disposed on the exhaust pipe, and the control method of the parallel exhaust control valve includes: when the first electromagnetic valve 111 is opened and the second electromagnetic valve 112 is closed, the parallel exhaust port 11 is communicated with the exhaust cavity through a parallel heat return pipe, and the exhaust of the parallel cylinder 1 enters the exhaust cavity and then is exhausted through the main exhaust port 10; the first electromagnetic valve 111 is closed, the second electromagnetic valve 112 is opened, the parallel exhaust port 11 is disconnected from the exhaust cavity, and the exhaust is directly carried out outwards.

The first exhaust port 21 and the exhaust cavity of the first varactor cylinder 2 are communicated with the exhaust cavity through a first heat return pipe, and meanwhile, the first exhaust port 21 can directly exhaust, namely, the first exhaust port 21 is simultaneously connected with the first heat return pipe and an exhaust pipe for directly exhausting, so that the first parallel cylinder 1 can exhaust to the exhaust cavity and can independently exhaust. A first control valve is provided at the first exhaust port 21 for controlling the first exhaust port 21 to communicate with the exhaust chamber or to exhaust independently. Preferably, the first control valve includes a third solenoid valve 211 disposed on the first heat return pipe, and a fourth solenoid valve 212 disposed on the exhaust pipe, and the control method of the first control valve includes: when the third electromagnetic valve 211 is opened and the fourth electromagnetic valve 212 is closed, the first exhaust port 21 is communicated with the exhaust cavity through the first heat return pipe; when the third electromagnetic valve 211 is closed and the fourth electromagnetic valve 212 is opened, the first exhaust port 21 is disconnected from the exhaust cavity, and the exhaust is directly carried out.

The second exhaust port 31 of the second varactor cylinder 3 is communicated with the exhaust cavity through a second heat return pipe, and meanwhile, the second exhaust port 31 can directly exhaust, namely, the second exhaust port 31 is simultaneously connected with the second heat return pipe and an exhaust pipe for directly exhausting, so that the second parallel cylinder 1 can exhaust to the exhaust cavity and can independently exhaust. A second control valve is provided at the second exhaust port 31 for controlling the second exhaust port 31 to communicate with the exhaust chamber or to exhaust independently. Preferably, the second control valve includes a third solenoid valve 211 disposed on the second heat-return pipe, and a sixth solenoid valve 312 disposed on the exhaust pipe, and the control means of the second control valve includes: when the fifth electromagnetic valve 311 is opened and the sixth electromagnetic valve 312 is closed, the second exhaust port 31 is communicated with the exhaust cavity through the second heat return pipe; when the fifth electromagnetic valve 311 is closed and the sixth electromagnetic valve 312 is opened, the second exhaust port 31 is disconnected from the exhaust chamber, and the exhaust is directly performed.

The structure of the exhaust port of each cylinder enables each cylinder to realize independent exhaust, so that any cylinder can realize independent operation of independent exhaust or multi-cylinder operation of independent exhaust of a plurality of cylinders; or it is also possible to realize that a plurality of cylinders are simultaneously exhausted through the exhaust chamber.

The volumes of the parallel cylinder 1, the first variable volume cylinder 2 and the second variable volume cylinder 3 are different, and preferably the volume ratio between the different cylinders is: the volume ratio of the parallel cylinder 1 to the first variable volume cylinder 2 is 0.08-0.6; the volume ratio of the first variable volume cylinder 2 to the second variable volume cylinder 3 is 0.4-0.9; the volume ratio of the parallel cylinder 1 to the second variable volume cylinder 3 is 0.15-0.85.

The capacity-variable principle of each cylinder is as follows: when the knockout sucks low-medium pressure gas, a part of gas is led to a variable-volume switching device (the scheme adopts a pin sliding vane mode), namely the lower end of the switching device is low-medium pressure gas, and when the low-medium pressure gas of the air suction port is led to the upper end of the switching device, the pressure balance is an unloading mode; when the high-pressure gas at the exhaust end is led to the upper end of the switching device, the pressure difference is established into an operation mode (the variable capacity control port is communicated with the air suction and exhaust port, and the air suction and exhaust pipeline is provided with an electromagnetic valve for controlling whether the gas flows or not).

In this embodiment, the three cylinders are all variable-capacity cylinders, and the volume ratio of each cylinder can be adjusted within a certain range so as to adapt to different working modes. The energy efficiency of the compressor is improved through the volume adjustment of the three cylinders, and the problems of vibration, APF and the like are improved. And the structure that sets up a plurality of gas vents can realize different exhaust modes, further improves the efficiency of compressor.

And adopt the heat return pipe structure for exhaust gas enters into the motor upper chamber through the heat return pipe, reduces gas flow resistance and pressure pulsation, when promoting compressor efficiency, dehumidification heating operating mode and effectively promoting the heating performance of-15 ℃ and large-span heating realization different demands, still can reduce vibration and the noise of compressor, the furthest promotion mechanical refrigeration's efficiency has very good market prospect.

In addition, the size of the cylinder body and the air suction and exhaust modes are adjusted, so that the vibration of the compressor is obviously reduced, the problem of large vibration of the large compressor caused by rotational inertia of the large compressor is avoided, and the energy efficiency of the compressor and the APF of an air conditioning system can be obviously improved while the cost of the compressor is reduced.

Example 2

In this embodiment, the present invention provides an air conditioning system, including the compressor assembly provided in the above embodiment, a communication pipeline is provided between the main exhaust port 10 of the exhaust chamber of the compressor and the air suction port of the parallel cylinder 1, and a parallel variable capacity dispenser 13 and a parallel variable capacity control valve 131 are provided on the communication pipeline; a communication pipeline is arranged between the main exhaust port 10 of the exhaust cavity and the air suction port of the first variable-volume cylinder 2, and a first variable-volume liquid separator 23 and a first variable-volume control valve 231 are arranged on the communication pipeline; a communication pipeline is arranged between the main exhaust port 10 of the exhaust cavity and the air suction port of the second variable-volume cylinder 3, and a parallel variable-volume liquid separator 13 and a second variable-volume control valve are arranged on the communication pipeline. The variable capacity dispensers and the variable capacity control valves are used for controlling the variable capacity of each cylinder.

The suction port of the parallel cylinder 1 is also in communication with the parallel dispenser 12, the suction port of the first variable volume cylinder is also in communication with the first dispenser 22, and the suction port of the second variable volume cylinder is also in communication with the second dispenser 32. A seventh solenoid valve 132 is arranged between the inlet end of the parallel variable capacity dispenser 13 and the inlet end of the parallel dispenser 12, an eighth solenoid valve 232 is arranged between the inlet end of the first variable capacity dispenser 23 and the inlet end of the first dispenser 22, and a ninth solenoid valve 332 is arranged between the inlet end of the second variable capacity dispenser 33 and the inlet end of the second dispenser 32.

The air conditioning system further comprises a first heat exchange part, a second heat exchange part, a reversing valve 4 and a flash evaporator 6, wherein the first heat exchange part and the second heat exchange part of the compressor and the reversing valve 4 are sequentially connected to form a refrigerant loop, and the reversing valve 4 is used for controlling the flow direction of a refrigerant.

The inlet end of the parallel liquid dispenser 12, the inlet end of the first liquid dispenser 22 and the inlet end of the second liquid dispenser 32 are connected to the same port of the reversing valve 4, a connecting pipe and a tenth electromagnetic valve 8 are arranged between the first liquid dispenser 22 and the second liquid dispenser 32 and a communication pipeline between the reversing valve 4, when the tenth electromagnetic valve 8 is closed, the first liquid dispenser 22 and the second liquid dispenser 32 independently enter air, and when the tenth electromagnetic valve 8 is opened or the air inlet channels of the first liquid dispenser 22 and the second liquid dispenser 32 are communicated, so that the air inlet temperatures of the first liquid dispenser 22 and the second liquid dispenser are consistent.

Wherein, the first port of flash vessel 6 is connected with the second end of first heat transfer portion, and the second port of flash vessel 6 is connected with parallel knockout 12, supplies air to parallel induction port through flash vessel 6. The third port of the flash vessel 6 is connected to the first end of the second heat exchanger 52. A first flash control valve 61 is provided between the first port of the flash evaporator 6 and the second end of the first heat exchange portion, and a second flash control valve 62 is provided between the second port of the flash evaporator 6 and the parallel liquid separator 12.

The first flash control valve 61 and the second flash control valve 62 are used for controlling whether the refrigerant flowing out of the first heat exchanging portion flows through the flash evaporator 6 or whether the refrigerant is supplied to the parallel suction port of the parallel cylinder 1 through the flash evaporator 6.

A refrigerant passage is provided in parallel with the flash evaporator 6 between the first heat exchange portion and the second heat exchange portion, and when the first flash control valve 61 is closed, the refrigerant flowing out of the first heat exchange portion may directly flow into the second heat exchange portion, or when the first flash control valve 61 is opened, part or all of the refrigerant flowing out of the first heat exchange portion flows through the flash evaporator 6 and then flows into the second heat exchange portion.

The parallel exhaust port 11, the first exhaust port 21, and the second exhaust port 31 are simultaneously connected to one port of the reversing valve 4, and the main exhaust port 10 is connected to the other port of the reversing valve 4, so that the compressor can exhaust in different exhaust modes, that is, by controlling the opening and closing states of the solenoid valves at the exhaust ports of the respective cylinders, the compressor can exhaust through the main exhaust port 10 or independently exhaust through the exhaust ports of the respective cylinders.

Preferably, the first heat exchange portion comprises four heat exchangers arranged in parallel, i.e. comprising: a first heat exchanger 51, a first end of the first heat exchanger 51 being provided with a first heat exchanging electromagnetic valve 511; the second heat exchanger 52, the first end of the second heat exchanger 52 is provided with a second heat exchange electromagnetic valve 521; the third heat exchanger 53, the first end of the third heat exchanger 53 is provided with a third heat exchange electromagnetic valve 531; the fourth heat exchanger 54, the first end of the fourth heat exchanger 54 is provided with a fourth heat exchange solenoid valve 541, and the first ends of the four heat exchangers are respectively connected to one port of the reversing valve 4 through the solenoid valves provided correspondingly. The second ends of the four heat exchangers of the first heat exchange part are simultaneously connected with the first port of the flash evaporator 6.

The second heat exchange part comprises four heat exchangers which are arranged in parallel, namely, the heat exchange part comprises: the fifth heat exchanger 71, the first end of the fifth heat exchanger 71 is provided with a fifth heat exchange electromagnetic valve 711; a sixth heat exchanger 72, a first end of the sixth heat exchanger 72 being provided with a sixth heat exchange solenoid valve 721; a seventh heat exchanger 73, a first end of the seventh heat exchanger 73 being provided with a seventh heat exchanging electromagnetic valve 731; the eighth heat exchanger 74, the first end of the eighth heat exchanger 74 is provided with an eighth heat exchange electromagnetic valve 741, and the first ends of the four heat exchangers are respectively provided with an electromagnetic valve for controlling the opening and closing of the first ends of the heat exchangers. The first ends of the four heat exchangers of the second heat exchange part are connected in parallel and then connected with the second end of the first heat exchange part or connected with the third port of the flash evaporator 6, and the second ends of the four heat exchangers of the second heat exchange part are connected to one port of the reversing valve 4.

Preferably, in this embodiment, the heat exchange efficiency of different heat exchangers is different, so that the heat exchangers can be used for different purposes, for example, a heat exchanger for an air conditioner and a heat exchanger for a water heater can be simultaneously set, the power of a plurality of heat exchangers is different, the parallel air cylinders 1 with small displacement can be operated for a small room air conditioner, and the operation of a large displacement double cylinder or a three cylinder can be used for a water heater.

Example 3

The present embodiment provides a control method for an air conditioning system according to the foregoing embodiment, where the compressor assembly is provided with the following operation modes according to different operation loads of the air conditioning system:

1. Single cylinder mode: taking the parallel cylinder 1 as an example, when only small-displacement operation is required, at the air inlet end of the compressor, the third variable-volume control valve 331, the first variable-volume control valve 231 and the seventh electromagnetic valve 132 are closed, and the ninth electromagnetic valve 332, the eighth electromagnetic valve 232 and the parallel variable-volume control valve 131 are opened; the exhaust port end closes the third solenoid valve 211, the fifth solenoid valve 311, the second solenoid valve 112, the fourth solenoid valve 212, and the sixth solenoid valve 312, and opens the first solenoid valve 111. At this time, the parallel cylinder 1 of the compressor is operated, the first variable capacity cylinder 2 and the second variable capacity cylinder 3 are unloaded, the discharged gas enters the exhaust cavity through the parallel exhaust port 11 and is then discharged through the reversing valve 4 by the main exhaust port 10, at this time, the third heat exchange electromagnetic valve 531 is opened, the first heat exchange electromagnetic valve 511, the second heat exchange electromagnetic valve 521 and the fourth heat exchange electromagnetic valve 541 are closed, and the gas enters the third heat exchanger 53. The first flash control valve 61 and the second flash control valve 62 are opened, the gas discharged from the third heat exchanger 53 enters the flash evaporator 6, and a part of the gas enters the parallel knockout 12 through the flash evaporator 6, and finally returns to the parallel cylinder 1. At the same time, the seventh heat exchange solenoid valve 731 is opened, the fifth heat exchange solenoid valve 711, the sixth heat exchange solenoid valve 721, and the eighth heat exchange solenoid valve 741 are closed, and a part of the gas in the flash evaporator 6 enters the seventh heat exchanger 73 through the seventh heat exchange solenoid valve 731. At this time, the tenth electromagnetic valve 8 is opened, the seventh heat exchanger 73 circulates the gas to the first and second variable capacity cylinders 2 and 3 to supply the low pressure gas, the first and second variable capacity cylinders 2 and 3 are unloaded, and the parallel cylinders 1 independently work to satisfy the low load demand heating amount.

In addition, the flow path of the original suction and exhaust mode is unchanged, and the first flash control valve 61 and the second flash control valve 62 are closed, so that the parallel cylinder 1 does not suck medium-pressure gas of the flash evaporator 6 any more, but the gas is directly circulated to the parallel cylinder 1 through the seventh heat exchanger 73, the volumetric efficiency is further reduced, and the heating capacity of lower load is met. Similarly, the first variable-capacity air cylinder 2 or the second variable-capacity air cylinder 3 can independently work under the control of the electromagnetic valve, so that the single-cylinder mode of different heating capacity requirements is met.

2. Double-cylinder single-row mode: taking the double cylinders of the first variable capacity cylinder 2 and the second variable capacity cylinder 3 as an example, when medium or large displacement operation is required, the air inlet end of the compressor opens the third variable capacity control valve 331, the first variable capacity control valve 231 and the seventh electromagnetic valve 132, and closes the ninth electromagnetic valve 332, the eighth electromagnetic valve 232 and the parallel variable capacity control valve 131; the exhaust port end closes the first solenoid valve 111, the second solenoid valve 112, the fourth solenoid valve 212, the sixth solenoid valve 312, and opens the third solenoid valve 211 and the fifth solenoid valve 311. At this time, the first variable-capacity cylinder 2 and the second variable-capacity cylinder 3 of the compressor run, the parallel variable-capacity cylinders are unloaded, the gas exhausted by the first variable-capacity cylinder 2 and the second variable-capacity cylinder 3 respectively enter into the upper cavity of the motor of the shell through the first exhaust port 21 and the second exhaust port 31, namely the exhaust cavity is exhausted by the main exhaust port 10, meanwhile, the first heat exchange electromagnetic valve 511 and the second heat exchange electromagnetic valve 521 are opened, the third heat exchange electromagnetic valve 531 and the fourth heat exchange electromagnetic valve 541 are closed, and the gas exhausted by the main exhaust port 10 enters into the first heat exchanger 51 and the second heat exchanger 52 through the reversing valve 4. The first flash control valve 61 and the second flash control valve 62 are opened, the gas discharged by the first heat exchanger 51 and the second heat exchanger 52 enters the flash evaporator 6, a part of the gas enters the parallel knockout 12 through the flash evaporator 6, and finally enters the parallel cylinder 1 to provide gas for unloading. The fifth heat exchange solenoid valve 711 and the sixth heat exchange solenoid valve 721 are opened, the seventh heat exchange solenoid valve 731, the eighth heat exchange solenoid valve 741 and the tenth solenoid valve 8 are closed, and accordingly, the fifth heat exchanger 71 and the sixth heat exchanger 72 circulate gas to the first variable volume cylinder 2 and the second variable volume cylinder 3, and the first variable volume cylinder 2 and the second variable volume cylinder 3 are operated (double temperature), and the parallel cylinder 1 is unloaded, thereby realizing double cylinder operation.

In addition, the flow path of the original suction and exhaust mode is unchanged, and the tenth electromagnetic valve 8 of the air inlet is opened, so that the first variable volume cylinder 2 and the second variable volume cylinder 3 suck the gas with the same temperature, and the heating capacity with lower load is met. Similarly, through the control of the electromagnetic valve, double-cylinder single-row modes (but only the main exhaust port 10 is finished) such as the second variable-capacity cylinder 3+parallel cylinder 1, the first variable-capacity cylinder 2+parallel cylinder 1 and the like can be realized, and different heating requirements are met.

3. Double-cylinder double-row mode: taking the double cylinders of the first variable-capacity cylinder 2 and the second variable-capacity cylinder 3 as examples, the operation principle is similar to that of the double-cylinder single-row mode, and only the exhaust port is reset in a flow path. In the mode, the third electromagnetic valve 211 and the fifth electromagnetic valve 311 are closed, the fourth electromagnetic valve 212 and the sixth electromagnetic valve 312 are opened, so that the gas of the big cylinder and the gas of the small cylinder are respectively discharged and enter into a circulation loop of the air conditioning system, the operation of the compressor and the air conditioning system is completed, the mode mainly can realize multiple modes such as dehumidification, refrigeration or heating according to requirements, the electromagnetic valves are controlled to select a condenser and an evaporator according to the requirements, and the step treatment is further improved. Similarly, the double-cylinder double-row mode of the second variable-capacity cylinder 3+parallel cylinder 1, the first variable-capacity cylinder 2+parallel cylinder 1 and the like can be realized through the control of the electromagnetic valve, so that different heating requirements are met.

4. Three-cylinder single-row operation mode: when the three cylinders all start to operate, the compressor air inlet end opens the third and first variable capacity control valves 331, 231 and the parallel variable capacity control valve 131, closes the ninth and eighth solenoid valves 332, 232 and 132, and the air outlet end closes the second and fourth solenoid valves 112, 212 and 312, and opens the first and third and fifth solenoid valves 111, 211 and 311. At this time, the three cylinders of the compressor are operated, and the discharged gas is introduced into the discharge chamber through the parallel discharge port 11, the first discharge port 21, and the second discharge port 31, and is discharged from the main discharge port 10. At the same time, the fourth heat exchange solenoid valve 541 is opened, the first heat exchange solenoid valve 511, the second heat exchange solenoid valve 521 and the third heat exchange solenoid valve 531 are closed, and the gas discharged from the main exhaust port 10 enters the fourth heat exchanger 54 through the reversing valve 4. The first flash control valve 61 and the second flash control valve 62 are opened, the gas discharged from the fourth heat exchanger 54 enters the flash evaporator 6, and a part of the gas enters the parallel knockout 12 through the flash evaporator 6 and finally enters the parallel cylinder 1 to provide gas. The eighth heat exchange solenoid valve 741 is opened, the fifth heat exchange solenoid valve 711, the sixth heat exchange solenoid valve 721, and the seventh heat exchange solenoid valve 731 are closed, and the other part of the gas in the flash evaporator 6 circulates the gas to the first and second varactor cylinders 2 and 3 through the eighth heat exchanger 74 (the tenth solenoid valve 8 is closed), and the first and second varactor cylinders 2 and 3 operate.

In addition, the flow path of the original suction and exhaust mode is unchanged, and the tenth electromagnetic valve 8 of the air inlet is opened, so that the first variable volume cylinder 2 and the second variable volume cylinder 3 suck the gas with the same temperature, and the heating capacity with lower load is met. The single-evaporator air conditioning system is subjected to stepped cooling, independent temperature and humidity control, and the heating capacity of the air conditioning system is obviously improved.

5. Three cylinder double row operation mode: when the three cylinders start to operate, the operation principle is similar to that of the three-cylinder single-row mode, and only the exhaust port is reset. In the original scheme, the first electromagnetic valve 111, the third electromagnetic valve 211 and the fifth electromagnetic valve 311 are opened, the discharged gas enters the corresponding heat exchangers through the main exhaust port 10, the mode is changed into a double exhaust structure, the matching of the double exhaust structure can be selected according to the heating capacity of the requirement (the cylinder body is different), the exhaust of the second variable capacity cylinder 3 is taken as an example, the first electromagnetic valve 111, the third electromagnetic valve 211 and the sixth electromagnetic valve 312 are opened, the fifth electromagnetic valve 311, the second electromagnetic valve 112 and the fourth electromagnetic valve 212 are closed, the gas of the first variable capacity cylinder 2+ and the gas of the second variable capacity cylinder 3 are respectively discharged into a circulation loop of an air conditioning system, the operation of the compressor and the air conditioning system is completed, the mode mainly comprises the steps of realizing multiple modes such as dehumidification, refrigeration or heating according to different heating capacity requirements, controlling the electromagnetic valves to select a condenser and an evaporator according to the requirement, and further improving the energy efficiency of the air conditioning system. Similarly, a plurality of modes such as double rows of the first variable-capacity cylinder 2, double rows of the parallel cylinders 1 and the like can be realized through the control of the electromagnetic valve.

6. Three-cylinder three-row operation mode: when the three cylinders start to operate, the operation principle is similar to that of the three-cylinder single-row mode, and only the exhaust port is reset. In the original scheme, the first electromagnetic valve 111, the third electromagnetic valve 211 and the fifth electromagnetic valve 311 are opened, the discharged gas enters the corresponding condenser and evaporator through the main exhaust port 10, the mode is changed into a three-exhaust mode, and the specific exhaust mode can be selected according to the heating capacity of the requirement (the cylinder body volume is different). Taking the exhaust of the parallel air cylinder 1 as an example, the first electromagnetic valve 111, the fourth electromagnetic valve 212 and the sixth electromagnetic valve 312 are opened, the third electromagnetic valve 211, the fifth electromagnetic valve 311 and the second electromagnetic valve 112 are closed, so that the air of the parallel air cylinder 1 is exhausted into the exhaust cavity and is exhausted through the main exhaust port 10, the first variable volume air cylinder 2 and the second variable volume air cylinder 3 are respectively exhausted through the first exhaust port 21 and the second exhaust port 31, and the air of the three flow paths is respectively and independently exhausted into the circulation loop of the air conditioning system, and the operation of the compressor and the air conditioning system is completed. The mode mainly can realize multiple modes such as dehumidification, refrigeration or heating according to different heating quantity demands, the electromagnetic valve is controlled to select the condenser and the evaporator according to the situation, step processing is carried out, and the energy efficiency of the air conditioning system is further improved.

Similarly, by controlling the electromagnetic valve, a plurality of modes such as three rows of first variable-volume cylinders 2, three rows of multi-temperature large cylinders and the like can be realized. The three-evaporator air conditioning system is subjected to stepped cooling, independent temperature and humidity control, and the heating capacity of the air conditioning system is obviously improved. The electromagnetic valve can be controlled in the same way, so that modes of three cylinders, four rows and the like are realized, and the switch of the tenth electromagnetic valve 8 can control whether the first variable-volume air cylinder 2 and the second variable-volume air cylinder 3 inhale multi-temperature or gas with the same temperature (the arrangement of a plurality of heat exchangers can freely realize a plurality of temperatures so as to meet different and various requirements).

According to different demands, the heat exchangers of cylinder bodies with different volumes are different, so that the flow path can be changed according to actual demands, and the use demands are met.

The multi-heat exchanger of the air conditioning system is characterized in that different heat exchangers are used for processing heating with different discharge capacities, processing loads in a grading manner and improving circulation efficiency. The air conditioning system not only can realize the cascade heating control of multiple evaporators and multiple condensers, but also can realize multiple heating electric device requirements according to different heating quantity requirements, realize multiple schemes such as single cylinder, double cylinders (multiple rows), three cylinders and the like according to the discharge capacity requirements, realize condensation reheating and do not need electric reheating.

The air conditioning system can be multiple in one, and one compressor can meet different electrical appliance demands (such as the small-displacement parallel air cylinder 1 provides an air conditioner for a small room, and the large-displacement double-cylinder or three-cylinder is used for a water heater), so that the requirements of customers can be met as much as possible.

Meanwhile, the design of the air conditioning system with multiple evaporation and multiple condensers also enables the temperature and humidity control to realize independent control, and different modes of control are realized for the air conditioning system according to different seasons and environments, so that not only can energy be saved, cost and space be reduced, but also one compressor can realize different electrical appliance requirements (such as a small-displacement parallel air cylinder 1 provides an air conditioner for a small room, and a large-displacement double cylinder or a three-cylinder is used for a water heater), the customer requirements can be met as much as possible, and the heating performance of the air conditioner can be remarkably improved.

Exemplary embodiments of the present disclosure are specifically illustrated and described above. It is to be understood that this disclosure is not limited to the particular arrangements, instrumentalities and methods of implementation described herein; on the contrary, the disclosure is intended to cover various modifications and equivalent arrangements included within the spirit and scope of the appended claims.

Claims

1. A compressor assembly, comprising: the compressor, be provided with in the casing of compressor:

2. The compressor assembly of claim 1, wherein a cylinder volume of the parallel cylinder is less than a cylinder volume of the first varactor cylinder, the cylinder volume of the first varactor cylinder being less than a cylinder volume of the second varactor cylinder.

3. The compressor assembly of claim 2, wherein a cylinder volume ratio of the parallel cylinder to the first varactor is 0.08-0.6.

4. The compressor assembly of claim 2, wherein a cylinder volume ratio of the first and second variable volume cylinders is 0.4-0.9.

5. The compressor assembly of claim 2, wherein a cylinder volume ratio of the parallel cylinder to the second varactor is 0.15-0.85.

6. The compressor assembly according to any one of claims 1 to 5, wherein upper and lower flanges are provided at ends of the parallel cylinder and the second variable volume cylinder, respectively, a partition is provided between the variable volume cylinder and the first variable volume cylinder,

7. The compressor assembly of any one of claims 1 to 5, wherein,

8. The compressor assembly of claim 7, wherein the suction port of the parallel cylinder is further in communication with a parallel knockout;

9. An air conditioning system comprising a first heat exchange portion, a second heat exchange portion, a reversing valve, a flash evaporator, and a compressor assembly according to any one of claims 1-8,

10. The air conditioning system of claim 9, further comprising a reversing valve,

11. The air conditioning system according to claim 10, wherein the first heat exchanging portion includes four heat exchangers arranged in parallel, the second heat exchanging portion includes four heat exchangers arranged in parallel, each of the heat exchangers is provided with a solenoid valve at a first end thereof,

12. A control method of an air conditioning system according to any of claims 9-11, characterized in that the compressor assembly is provided with the following modes of operation depending on the operating load of the air conditioning system: