CN112727768A

CN112727768A - Double-two-stage rolling rotor type compressor and air conditioning system

Info

Publication number: CN112727768A
Application number: CN201910975156.4A
Authority: CN
Inventors: 张利; 熊俊; 周易
Original assignee: Shanghai Highly Electrical Appliances Co Ltd
Current assignee: Shanghai Highly Electrical Appliances Co Ltd
Priority date: 2019-10-14
Filing date: 2019-10-14
Publication date: 2021-04-30

Abstract

The invention discloses a double two-stage rolling rotor type compressor and an air conditioning system, wherein the compressor comprises: the compressor comprises a shell, a first two-stage compression unit and a second two-stage compression unit, wherein the first two-stage compression unit and the second two-stage compression unit are arranged in the shell; the first two-stage compression unit performs first-stage compression and second-stage compression on the low-temperature low-pressure refrigerant introduced into the first two-stage compression unit to obtain a high-temperature high-pressure refrigerant and discharges the high-temperature high-pressure refrigerant; the second two-stage compression unit performs one-stage and two-stage compression on the introduced low-temperature low-pressure refrigerant to obtain a high-temperature high-pressure refrigerant and discharges the high-temperature high-pressure refrigerant. The direction of the low-temperature low-pressure refrigerant introduced into the first two-stage compression unit is opposite to that of the low-temperature low-pressure refrigerant introduced into the second two-stage compression unit, and the direction of the low-temperature low-pressure refrigerant which flows out of the first two-stage compression unit and flows out of the second two-stage compression unit and is compressed by one stage is opposite to that of the low-temperature low-pressure refrigerant.

Description

Double-two-stage rolling rotor type compressor and air conditioning system

Technical Field

The invention relates to the field of air conditioners, in particular to a double-two-stage rolling rotor type compressor and an air conditioning system.

Background

The compressor is a fluid machine for lifting low-pressure gas into high-pressure gas, and is a heart of a refrigeration system. Among them, the rolling rotor type compressor using a rotational force is dominant in a small capacity air conditioning unit due to its relatively low manufacturing cost and relatively high performance.

With the further expansion of the discharge capacity of the rotary roller type compressor and the development of the downstream application market, the competition of the price, the technology and the like of the light commercial air conditioner compressor product is always the diffusion of the smoke, but the current situation is that the market of 5 or more commercial machines is still dominated by the scroll compressor because the scroll compressor has advantages in the aspects of capacity and energy efficiency. The cost of the scroll compressor is always high, which leads to higher selling price of the commercial machine of 5 or more, and influences further expansion of the market for a long time. Therefore, it is urgently needed to develop a low-cost and energy-efficient rotor compressor to replace a scroll compressor so as to reduce the manufacturing cost of the multi-split air-conditioning system.

The rolling rotor type compressor commonly used at present includes two types, i.e., a single-rotor compressor and a dual-rotor compressor (a two-stage rolling rotor compressor), in which the resultant force of gas of the single-rotor compressor and the dual-rotor compressor is unbalanced to the acting force of a crankshaft (the resultant force of gas borne by the crankshaft) for driving a piston in a cylinder to rotate, the resultant force of gas borne by the crankshaft is specifically shown in fig. 1, which specifically shows that the magnitude of the resultant force of gas borne by the crankshaft varies with the rotation angle of the crankshaft, and the crankshaft is bent and deformed due to the imbalance of the resultant force of gas borne by the crankshaft, and the bent and deformed crankshaft may cause adverse effects on fit clearances between various components inside the compressor, for example, when the crankshaft is bent and deformed, an eccentric portion on the crankshaft may drive the piston to tilt and bend, possibly causing the compressor to stall, which in turn results in a reduction in the reliability of the compressor and its refrigeration performance.

In addition, in the conventional two-stage rolling rotor compressor, the increase in the capacity (cooling capacity) of the two-stage rolling rotor compressor causes an increase in the size of the cylinder, but the increase in the capacity of the two-stage rolling rotor compressor is difficult to achieve by this method depending on the structural size of the entire compressor. Further, in the prior art, it is difficult to further improve the efficiency of the compressor.

Disclosure of Invention

The invention aims to provide a double-two-stage rolling rotor type compressor and an air conditioning system, which are used for solving the problem of unbalanced resultant force of gas borne by a crankshaft of the compressor in the prior art, and achieving the purposes of improving the stress state of the crankshaft, reducing the abrasion of the crankshaft and improving the reliability of the compressor; meanwhile, the invention can also greatly improve the refrigerating capacity of the compressor and improve the volumetric efficiency of the compressor; the air suction temperature and the exhaust temperature of the secondary compression can be reduced, and the performance of the compressor and the performance of an air conditioner are improved.

In order to solve the above problems and achieve the above objects, the present invention is implemented by the following technical solutions:

a dual two-stage rolling rotor compressor comprising: the casing sets up first two-stage compression unit and second two-stage compression unit inside the casing:

the first two-stage compression unit comprises a first compression subunit and a second compression subunit, and the first compression subunit is communicated with the second compression subunit through a communication path;

the second two-stage compression unit comprises a third compression subunit and a fourth compression subunit, and the third compression subunit is communicated with the fourth compression subunit through a communication path;

one compression subunit in the first two-stage compression unit is used as a first-stage compression unit and is used for introducing a low-temperature low-pressure refrigerant and performing first-stage compression on the low-temperature low-pressure refrigerant;

the other compression sub-unit in the first two-stage compression unit is used as a second-stage compression unit and is used for carrying out two-stage compression on the low-temperature low-pressure refrigerant after the first-stage compression to obtain a high-temperature high-pressure refrigerant and discharging the high-temperature high-pressure refrigerant;

one compression subunit in the second two-stage compression unit is used as a first-stage compression unit and is used for introducing a low-temperature low-pressure refrigerant and performing one-stage compression on the low-temperature low-pressure refrigerant;

the other compression sub-unit in the second two-stage compression unit is used as a second-stage compression unit and is used for performing two-stage compression on the low-temperature low-pressure refrigerant subjected to the one-stage compression to obtain a high-temperature high-pressure refrigerant and discharging the high-temperature high-pressure refrigerant;

the direction of the low-temperature and low-pressure refrigerant introduced into the first-stage compression unit in the first two-stage compression unit is opposite to the direction of the low-temperature and low-pressure refrigerant introduced into the first-stage compression unit in the second two-stage compression unit;

a direction of the low-temperature and low-pressure refrigerant, which is compressed by one stage and flows in from the second-stage compression unit of the first two-stage compression unit, is opposite to a direction of the low-temperature and low-pressure refrigerant, which is compressed by one stage and flows in from the second-stage compression unit of the second two-stage compression unit.

Further, the method also comprises the following steps: and a cooling device disposed on a communication path between the first compression sub-unit and the second compression sub-unit and/or a communication path between the third compression sub-unit and the fourth compression sub-unit, wherein the cooling device is configured to cool the low-temperature low-pressure refrigerant, which flows through the communication path and is subjected to the first-stage compression.

Furthermore, the first compression subunit, the second compression subunit, the third compression subunit and the fourth compression subunit are sequentially arranged inside the shell according to the axial diameter direction of the shell.

Further, the double two-stage rolling rotor compressor further includes: the setting is in the inside bent axle of casing to and the interval sets up first eccentric part, second eccentric part, third eccentric part and fourth eccentric part on the bent axle, first eccentric part the second eccentric part the third eccentric part with the eccentric direction of fourth eccentric part differs 180 in proper order.

Further, the first eccentric portion, the second eccentric portion, the third eccentric portion, and the fourth eccentric portion are integrally formed with the crankshaft.

Further, the first compressing subunit includes: the device comprises a first cylinder cover, a first cylinder, a first middle plate, a first blade and a first piston, wherein the first blade and the first piston are arranged in the first cylinder; one end of the crankshaft penetrates through the first cylinder cover;

the first cylinder is arranged between the first cylinder cover and the first middle plate, and the first piston is sleeved outside the first eccentric part;

the head of the first blade is in contact with the surface of the first piston and is used for dividing the inner space of the first cylinder into a first suction cavity and a first exhaust cavity during the working process of the compressor;

and the first air cylinder is provided with a first air suction hole communicated with the first air suction cavity and a first air exhaust hole communicated with the first air exhaust cavity.

Further, the second compressing subunit includes: the first middle plate, a second cylinder positioned on one side of the first middle plate, which is far away from the first cylinder, a second middle plate, and a second blade and a second piston which are arranged in the second cylinder;

the second cylinder is arranged between the first middle plate and the second middle plate, and the second piston is sleeved outside the second eccentric part;

the head of the second vane contacts with the surface of the second piston, and is used for dividing the inner space of the second cylinder into a second suction cavity and a second discharge cavity during the operation of the compressor;

and a second air suction hole communicated with the second air suction cavity and a second air exhaust hole communicated with the second air exhaust cavity are formed in the second air cylinder.

Further, the third compressing subunit includes: the second middle plate, a third cylinder and a third middle plate are positioned on one side of the second middle plate, which is far away from the second cylinder, and a third blade and a third piston are arranged in the third cylinder;

the third cylinder is arranged between the second middle plate and the third middle plate, and the third piston is sleeved outside the third eccentric part;

the head of the third vane contacts with the surface of the third piston, and is used for dividing the inner space of the third cylinder into a third suction cavity and a third exhaust cavity during the operation of the compressor;

and a third air suction hole communicated with the third air suction cavity and a first exhaust port communicated with the third exhaust cavity are formed in the third air cylinder.

Further, the fourth compressing subunit includes: the third middle plate, a fourth cylinder positioned on one side of the third middle plate, which is far away from the third cylinder, a second cylinder cover, a fourth blade and a fourth piston which are arranged in the fourth cylinder;

the other end of the crankshaft penetrates through the second cylinder cover;

the fourth cylinder is arranged between the third middle plate and the second cylinder cover, and the fourth piston is sleeved outside the fourth eccentric part;

the head of the fourth vane is in contact with the surface of the fourth piston, and is used for dividing the inner space of the fourth cylinder into a fourth suction cavity and a fourth discharge cavity during the operation of the compressor;

and a fourth air suction hole communicated with the fourth air suction cavity and a first exhaust port communicated with the fourth exhaust cavity are formed in the fourth air cylinder.

Further, the air suction directions of the first air suction port, the second air suction port, the third air suction port and the fourth air suction port are sequentially different by 180 °.

Further, the exhaust directions of the first exhaust port, the second exhaust port, the third exhaust port and the fourth exhaust port are sequentially different by 180 °.

Further, the double two-stage rolling rotor compressor further includes: and the liquid distributors are respectively connected with the second air suction cavity and the third air suction cavity and are used for respectively providing the low-temperature and low-pressure refrigerant for the second air cylinder and the third air cylinder.

Further, the cooling device further includes: a first bend and a second bend; the first elbow communicates the first compression sub-unit with the second compression sub-unit; the second elbow pipe is communicated with the third compression subunit and the fourth compression subunit; particularly, the first elbow is used for communicating the second exhaust cavity with the first air suction cavity; the second elbow is used for communicating the third exhaust cavity with the fourth air suction cavity.

Optionally, the cooling device further comprises several coolers arranged on the first bend and/or the second bend.

Further, the first middle plate is provided with a first air path communicated with the second exhaust cavity; one end of the first elbow is communicated with the first air passage, and the other end of the first elbow is communicated with the first air suction cavity;

the third middle plate is provided with a second air path communicated with the third exhaust cavity; one end of the second elbow is communicated with the second gas path, and the other end of the second elbow is communicated with the fourth gas suction cavity.

In another aspect, the present invention also provides an air conditioning system, comprising: a condenser, a throttle valve and an evaporator, which are communicated in sequence, and a double two-stage rolling rotor compressor as described above;

the shell of the double two-stage rolling rotor compressor is communicated with the condenser, and the evaporator is communicated with the liquid distributor of the double two-stage rolling rotor compressor;

the double two-stage rolling rotor compressor is used for compressing the low-temperature low-pressure refrigerant to obtain a high-temperature high-pressure refrigerant;

the condenser is used for releasing heat of the high-temperature high-pressure refrigerant to obtain a high-temperature high-pressure liquid refrigerant;

the throttling valve is used for throttling the high-temperature high-pressure liquid refrigerant to obtain a low-temperature low-pressure liquid refrigerant;

the evaporator is used for evaporating and absorbing heat for the low-temperature low-pressure liquid refrigerant to obtain the low-temperature low-pressure refrigerant, and the low-temperature low-pressure refrigerant flows back to the liquid separator to be used for the next refrigeration cycle.

Compared with the prior art, the invention has the following advantages:

the invention relates to a double two-stage rolling rotor compressor, which comprises: the casing sets up first two-stage compression unit and second two-stage compression unit inside the casing: the first two-stage compression unit comprises a first compression subunit and a second compression subunit which are communicated with each other; the first two-stage compression unit comprises a first compression subunit and a second compression subunit, and the first compression subunit is communicated with the second compression subunit through a communication path; the second two-stage compression unit comprises a third compression subunit and a fourth compression subunit, and the third compression subunit is communicated with the fourth compression subunit through a communication path; one compression subunit in the first two-stage compression unit is used as a first-stage compression unit and is used for introducing a low-temperature low-pressure refrigerant and performing first-stage compression on the low-temperature low-pressure refrigerant; the other compression sub-unit in the first two-stage compression unit is used as a second-stage compression unit and is used for carrying out two-stage compression on the low-temperature low-pressure refrigerant after the first-stage compression to obtain a high-temperature high-pressure refrigerant and discharging the high-temperature high-pressure refrigerant; one compression subunit in the second two-stage compression unit is used as a first-stage compression unit and is used for introducing a low-temperature low-pressure refrigerant and performing one-stage compression on the low-temperature low-pressure refrigerant; the other compression sub-unit in the second two-stage compression unit is used as a second-stage compression unit and is used for performing two-stage compression on the low-temperature low-pressure refrigerant subjected to the one-stage compression to obtain a high-temperature high-pressure refrigerant and discharging the high-temperature high-pressure refrigerant; the direction of the low-temperature and low-pressure refrigerant introduced into the first-stage compression unit in the first two-stage compression unit is opposite to the direction of the low-temperature and low-pressure refrigerant introduced into the first-stage compression unit in the second two-stage compression unit; a direction of the low-temperature and low-pressure refrigerant, which is compressed by one stage and flows in from the second-stage compression unit of the first two-stage compression unit, is opposite to a direction of the low-temperature and low-pressure refrigerant, which is compressed by one stage and flows in from the second-stage compression unit of the second two-stage compression unit. The direction of the low-temperature and low-pressure refrigerant introduced into the first-stage compression unit in the first two-stage compression unit is opposite to the direction of the low-temperature and low-pressure refrigerant introduced into the first-stage compression unit in the second two-stage compression unit; the direction of the low-temperature and low-pressure refrigerant which flows into the second-stage compression unit in the first two-stage compression unit and is subjected to one-stage compression is opposite to that of the low-temperature and low-pressure refrigerant which flows into the second-stage compression unit in the second two-stage compression unit and is subjected to one-stage compression, namely the second air suction port, the second air exhaust port, the fourth air suction port and the fourth air exhaust port are constantly kept in the same direction, and the first air suction port, the first air exhaust port, the third air suction port and the third air exhaust port are constantly kept in the same direction, so that the gas resultant force on a crankshaft of the double-two-stage rolling rotor compressor is close to zero or equal to zero, the stress state of the crankshaft is improved, the abrasion of the crankshaft is reduced, and.

The invention realizes the purposes of improving the discharge capacity (capacity or refrigerating capacity) of the rolling rotor type compressor, improving the volumetric efficiency of the rolling rotor type compressor and improving the refrigerating capacity of the rolling rotor type compressor by adding the one-stage and two-stage compression unit.

The invention also cools the low-temperature low-pressure refrigerant after the first-stage compression by the added cooling device, which effectively reduces the temperature of the low-temperature low-pressure refrigerant after the first-stage compression, thereby reducing the suction temperature and the exhaust temperature when the low-temperature low-pressure refrigerant after the first-stage compression is subjected to the second-stage compression subsequently, further realizing the improvement of the compression performance of the rolling rotor compressor and improving the performance of an air conditioning system with the double two-stage rolling rotor compressor. In addition, the first compression subunit, the second compression subunit, the third compression subunit and the fourth compression subunit are sequentially arranged in the shell in the axial diameter direction of the shell, so that the purposes of improving the displacement (capacity or refrigerating capacity) of the rolling rotor type compressor and improving the refrigerating capacity of the rolling rotor type compressor can be realized under the condition of not increasing the transverse size of the whole compressor.

Drawings

Fig. 1 is a schematic structural diagram of a crankshaft of a dual two-stage rolling rotor compressor according to an embodiment of the present invention;

fig. 2 is a schematic diagram of a main structure of a dual two-stage rolling rotor compressor according to an embodiment of the present invention;

fig. 3 is a schematic view of a main structure of a dual two-stage rolling rotor compressor according to another embodiment of the present invention;

fig. 4 is a schematic diagram of a main structure of an air conditioning system according to an embodiment of the present invention;

fig. 5a is a schematic top view of a cylinder structure of a first compression unit of a dual two-stage rolling rotor compressor according to an embodiment of the present invention;

fig. 5b is a schematic top view of a cylinder structure of a second compression unit of a dual two-stage rolling rotor compressor according to an embodiment of the present invention;

fig. 6a is a schematic top view of a cylinder structure of a third compression unit of a dual two-stage rolling rotor compressor according to an embodiment of the present invention;

fig. 6b is a schematic top view of a cylinder structure of a fourth compression unit of a dual two-stage rolling rotor compressor according to an embodiment of the present invention;

fig. 7 is a schematic diagram comparing the magnitude of resultant gas force borne by the crankshaft of the dual two-stage rolling rotor compressor according to an embodiment of the present invention with that of the prior art rolling rotor compressor, with the change of the rotation angle of the crankshaft.

The reference numerals are explained below:

100-a housing; 101-an exhaust pipe; 200-a motor; 300-a crankshaft; 301-a first eccentric portion; 302-a second eccentric portion; 303-third eccentric portion; 304-a fourth eccentric portion; 401-a first muffler; 402-a second muffler; 500-a first compression subunit; 510-a second compression subunit; 520-a third compression subunit; 530-a fourth compression subunit; 501-a first cylinder cover; 502-a second cylinder head; 511-a first cylinder; 512-a second cylinder; 513-a third cylinder; 514-fourth cylinder; 521-a first piston; 522-a second piston; 523-third piston; 524-a fourth piston; 531-first intermediate plate; 532-a second intermediate plate; 533-a third intermediate plate; 600-a liquid separator; 701-a first elbow; 702-a second elbow; 710-a first cooler; 720-a second cooler; 801-a first blade; 802-a second blade; 803-third blade; 804-a fourth blade; 5110-first suction port; 5111-first exhaust; 5112-a first suction cavity; 5113-first venting cavity; 5120-second air entry; 5121-a second vent; 5122-a second aspiration lumen; 5123-a second venting chamber; 5130-third aspiration entry; 5131-third vent; 5132-third aspiration lumen; 5133-third venting chamber; 5140-fourth suction port; 5141-fourth vent; 5142-fourth aspiration lumen; 5143-a fourth venting chamber; 910-a condenser; 920-a throttle valve; 930-evaporator.

Detailed Description

The following describes in more detail embodiments of the present invention with reference to the schematic drawings. Advantages and features of the present invention will become apparent from the following description and claims. It is to be noted that the drawings are in a very simplified form and are not to precise scale, which is merely for the purpose of facilitating and distinctly claiming the embodiments of the present invention.

In the interest of clarity, not all features of an actual implementation are described. In the following description, well-known functions or constructions are not described in detail since they would obscure the invention in unnecessary detail. It will of course be appreciated that in the development of any such actual embodiment, numerous implementation-specific details must be set forth in order to achieve the developer's specific goals, such as compliance with system-related and business-related constraints, which will vary from one implementation to another. Moreover, it will be appreciated that such a development effort might be complex and time-consuming, but would nevertheless be a routine undertaking for those of ordinary skill in the art.

It is to be noted that the drawings are in a very simplified form and employ non-precise ratios for the purpose of facilitating and distinctly facilitating the description of one embodiment of the present invention. In this document, relational terms such as first and second, and the like may be used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Also, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the phrase "comprising an … …" does not exclude the presence of other identical elements in a process, method, article, or apparatus that comprises the element.

The core idea of the invention is to provide a double-two-stage rolling rotor type compressor and an air conditioning system, which are used for improving the stress state of a crankshaft and reducing the abrasion of the crankshaft, thereby improving the reliability of the compressor; meanwhile, the refrigeration capacity of the compressor can be greatly improved, and the volume efficiency of the compressor is improved; and the suction temperature and the exhaust temperature of the secondary compression can be reduced, and the performance of the compressor and the performance of an air conditioner are improved.

Specifically, as shown in fig. 2, fig. 5a, fig. 5b, fig. 6a and fig. 6b, the dual two-stage rolling rotor compressor of the present embodiment includes: a casing 100, a first two-stage compression unit (not numbered in fig. 3) and a second two-stage compression unit (not numbered in fig. 3) disposed inside the casing 100: the first two-stage compression unit includes a first compression sub-unit (not numbered in fig. 3) and a second compression sub-unit (not numbered in fig. 3) that are communicated with each other through a communication path; the second two-stage compression unit includes a third compression sub-unit (not numbered in fig. 3) and a fourth compression sub-unit (not numbered in fig. 3) that are communicated with each other through a communication path; one compression subunit in the first two-stage compression unit is used as a first-stage compression unit and is used for introducing a low-temperature low-pressure refrigerant and performing first-stage compression on the low-temperature low-pressure refrigerant; the other compression sub-unit in the first two-stage compression unit is used as a second-stage compression unit and is used for carrying out two-stage compression on the low-temperature low-pressure refrigerant after the first-stage compression to obtain a high-temperature high-pressure refrigerant and discharging the high-temperature high-pressure refrigerant; one compression subunit in the second two-stage compression unit is used as a first-stage compression unit and is used for introducing a low-temperature low-pressure refrigerant and performing one-stage compression on the low-temperature low-pressure refrigerant; the other compression sub-unit in the second two-stage compression unit is used as a second-stage compression unit and is used for performing two-stage compression on the low-temperature low-pressure refrigerant subjected to the one-stage compression to obtain a high-temperature high-pressure refrigerant and discharging the high-temperature high-pressure refrigerant; the direction of the low-temperature and low-pressure refrigerant introduced into the first-stage compression unit in the first two-stage compression unit is opposite to the direction of the low-temperature and low-pressure refrigerant introduced into the first-stage compression unit in the second two-stage compression unit; a direction of the low-temperature and low-pressure refrigerant, which is compressed by one stage and flows in from the second-stage compression unit of the first two-stage compression unit, is opposite to a direction of the low-temperature and low-pressure refrigerant, which is compressed by one stage and flows in from the second-stage compression unit of the second two-stage compression unit. Therefore, in the embodiment, by arranging the two-stage compression units, the displacement (capacity or refrigerating capacity) of the rolling rotor compressor is improved, the volumetric efficiency of the rolling rotor compressor is increased, the refrigerating capacity of the rolling rotor compressor is improved, the low-temperature and low-pressure refrigerant subjected to the first-stage compression is cooled by the added cooling device, the temperature of the low-temperature and low-pressure refrigerant subjected to the first-stage compression is effectively reduced, the suction temperature and the exhaust temperature during the subsequent second-stage compression of the low-temperature and low-pressure refrigerant subjected to the first-stage compression can be reduced, the compression performance and the working efficiency of the rolling rotor compressor are improved, and the performance of the air conditioning system with the two-stage rolling rotor compressor is improved. The direction of the low-temperature low-pressure refrigerant introduced into the first-stage compression unit in the first two-stage compression unit is opposite to the direction of the low-temperature low-pressure refrigerant introduced into the first-stage compression unit in the second two-stage compression unit; the direction of the low-temperature and low-pressure refrigerant which flows into the second-stage compression unit in the first two-stage compression unit and is subjected to one-stage compression is opposite to the direction of the low-temperature and low-pressure refrigerant which flows into the second-stage compression unit in the second two-stage compression unit and is subjected to one-stage compression, namely the second air suction port, the second air exhaust port, the fourth air suction port and the fourth air exhaust port are constantly kept in the same direction, and the first air suction port, the first air exhaust port, the third air suction port and the third air exhaust port are constantly kept in the same direction, so that the resultant force of the gas on the crankshaft of the double-two-stage rolling rotor compressor is close to zero or equal to zero, the stress state of the crankshaft is improved, the abrasion of the crankshaft is reduced.

Further, the first compression subunit, the second compression subunit, the third compression subunit and the fourth compression subunit are sequentially arranged inside the casing 100 according to the axial-radial direction (from top to bottom) of the casing. Therefore, in the embodiment, the first compression subunit, the second compression subunit, the third compression subunit and the fourth compression subunit are arranged inside the shell 100 from top to bottom, so that the displacement (capacity or refrigerating capacity) of the rolling rotor compressor is increased, the volumetric efficiency of the rolling rotor compressor is increased, and the refrigerating capacity of the rolling rotor compressor is improved under the condition that the transverse size of the whole compressor is not increased.

Further, please refer to fig. 1, the dual two-stage rolling rotor compressor further includes: a crankshaft 300 disposed inside the housing, and a first eccentric portion 301, a second eccentric portion 302, a third eccentric portion 303, and a fourth eccentric portion 304 disposed at intervals on the crankshaft 300. Specifically, the first eccentric portion 301, the second eccentric portion 302, the third eccentric portion 303 and the fourth eccentric portion 304 may be integrally formed with the crankshaft 300, so that the manufactured structure has better overall strength and is easy and convenient to install. In addition, the first eccentric portion 301, the second eccentric portion 302, the third eccentric portion 303 and the fourth eccentric portion 304 may be detachably and fixedly connected with the crankshaft 300. The fixed connection mode is convenient to maintain when the four eccentric parts have the problems of failure or damage.

Further, the eccentric directions of the first eccentric portion 301, the second eccentric portion 302, the third eccentric portion 303 and the fourth eccentric portion 304 are sequentially different by 180 °. The position arrangement can increase the balance capacity when the crankshaft 300 rotates, and increase the stress balance of the double two-stage rolling rotor compressor.

With continuing reference to fig. 1, 2 and 4, the first compressing subunit includes: a first cylinder head 501, a first cylinder 511, a first vane 801, a first piston 521 and a first intermediate plate 531 provided on the first cylinder 511, which are provided inside the housing 100; the upper part (one end) of the crankshaft 300 penetrates the first cylinder head 501; that is, the first cylinder head 501 may serve as a bearing for supporting the upper portion of the crankshaft 300.

The first cylinder 511 and the first piston 521 are disposed between the first cylinder head 501 and the first middle plate 531, the first piston 521 is sleeved outside the first eccentric portion 301, so that the first eccentric portion 301 is located inside the first piston 521, and the first piston 521 is eccentrically disposed inside the first cylinder 511.

The head of the first vane 801 is in contact with the surface of the first piston 521 for dividing the inner space of the first cylinder 511 into two parts of a first suction chamber 5112 and a first discharge chamber 5113 during the operation of the dual two-stage rolling rotor type compressor.

Further, the first cylinder 511 is provided with a first air intake port 5110 communicated with the first air intake chamber 5112 and a first air exhaust port 5111 communicated with the first air exhaust chamber 5113; the first suction port 5110 and the first discharge port 5111 are disposed adjacent to the first blade 801; the first suction port 5110 is located at one side of the first blade 801 and the first discharge port 5111 is located at the other side of the first blade 801. Theoretically, the closer the first suction port 5110 and the first discharge port 5111 are to the first blade 801, the more desirable the operation of the dual two-stage drum rotor type compressor is, and thus it is known that the above arrangement can improve the operation performance of the dual two-stage drum rotor type compressor.

Further, in this embodiment, the second compressing subunit includes: the first middle plate 531, a second cylinder 512 disposed inside the housing 100 and below the first middle plate 531, a second blade 802 disposed on the second cylinder 512, a second piston 522, and a second middle plate 532 in sequence; the second cylinder 512 and the second piston 522 are disposed between the first intermediate plate 531 and the second intermediate plate 532; the second piston 522 is sleeved outside the second eccentric portion 302, such that the second eccentric portion 302 is located inside the second piston 522, and the second piston 522 is eccentrically disposed inside the second cylinder 512.

The head of the second vane 802 is in contact with the surface of the second piston 522 for dividing the inner space of the second cylinder 512 into two parts of a second suction chamber 5122 and a second discharge chamber 5123 during the operation of the dual two-stage roller rotor type compressor.

The second cylinder 512 is provided with a second suction port 5120 communicated with the second suction chamber 5122 and a second exhaust port 5121 communicated with the second exhaust chamber 5123; the second suction port 5120 and the second discharge port 5121 are disposed adjacent to the second blade 802; the second suction port 5120 is located at one side of the second vane 802, and the second discharge port 5121 is located at the other side of the second vane 802; in theory, it is understood that the closer the second suction port 5120 and the second discharge port 5121 are to the second vane 802, the more desirable the operation of the dual two-stage drum rotor type compressor is, and thus the above arrangement can improve the operation performance of the dual two-stage drum rotor type compressor.

The second suction port 5120 is used for introducing the low-temperature and low-pressure refrigerant; the second discharge port 5121 is used for discharging the low-temperature and low-pressure refrigerant compressed by one stage; the second discharge port 5121 is connected to the first suction port 5110 such that the second discharge chamber 5123 communicates with the first suction chamber 5112; the first suction port 5110 is used for flowing the low-temperature and low-pressure refrigerant after being compressed by one stage; the first exhaust port 5111 is configured to discharge the high-temperature and high-pressure refrigerant to the outside of the casing 100 through the first cylinder head 501 (where a vent through hole communicating with the casing 100 may be provided on the first cylinder head 501 to discharge the high-temperature and high-pressure refrigerant to the outside of the casing 100 through the inside of the casing 100).

Further, the third compressing subunit described in this embodiment includes: the second intermediate plate 532, and a third cylinder 513, a third vane 803, a third piston 523 and a third intermediate plate 533 which are sequentially disposed inside the housing 100 and below the second intermediate plate 532, and which are disposed on the third cylinder 513; the third cylinder 513 and the third piston 523 are disposed between the second intermediate plate 532 and the third intermediate plate 533; the third piston 523 is sleeved outside the third eccentric part 303, so that the third eccentric part 303 is located inside the third piston 523, and the third piston 523 is eccentrically arranged inside the third cylinder 513; the head of the third vane 803 contacts the surface of the third piston 523 to divide the inner space of the third cylinder 513 into two parts, i.e., a third suction chamber 5132 and a third discharge chamber 5133, during the operation of the dual two-stage rolling rotor compressor.

The third cylinder 513 is provided with a third suction port 5130 communicated with the third suction chamber 5132 and a third exhaust port 5131 communicated with the third exhaust chamber 5133; the third suction port 5130 and the third discharge port 5131 are provided near the third blade 803; the third suction port 5130 is located at one side of the third blade 803, and the third discharge port 5131 is located at the other side of the third blade 803. In theory, the closer the third suction port 5130 and the third discharge port 5131 are to the third vane 803, the more desirable the operation of the dual two-stage drum rotor type compressor is, and thus it is understood that the above arrangement can improve the operation performance of the dual two-stage drum rotor type compressor.

Further, the fourth compressing subunit described in this embodiment includes: the third middle plate 533, and a fourth cylinder 514, a fourth vane 804, a fourth piston 524 and a second cylinder cover 502 which are sequentially disposed inside the housing 100 and below the third middle plate 533, the fourth vane 804 disposed on the fourth cylinder 514; a lower portion of the crankshaft 300 penetrates the second head 502; the second cylinder head 502 may serve as a bearing supporting the lower portion of the crankshaft 300.

The fourth cylinder 514 and the fourth piston 524 are disposed between the third intermediate plate 533 and the second cylinder head 502; the fourth piston 524 is sleeved outside the fourth eccentric portion 304, such that the fourth eccentric portion 304 is located inside the fourth piston 524, and the fourth piston 524 is eccentrically disposed inside the fourth cylinder 514; the head of the fourth vane 804 contacts the surface of the fourth piston 524 to divide the inner space of the fourth cylinder 514 into two parts, i.e., a fourth suction chamber 5142 and a fourth discharge chamber 5143, during the operation of the dual two-stage rolling rotor type compressor.

The fourth cylinder 514 is provided with a fourth suction port 5140 communicating with the fourth suction chamber 5142 and a fourth discharge port 5141 communicating with the fourth discharge chamber 5143.

The fourth suction port 5140 and the fourth discharge port 5141 are disposed adjacent to the fourth blade 804.

Further, the fourth suction port 5140 is located at one side of the fourth blade 804, and the fourth discharge port 5141 is located at the other side of the fourth blade 804. In theory, the closer the fourth suction port 5140 and the fourth discharge port 5141 are to the fourth vane 804, the more desirable the operation of the dual two-stage drum rotor type compressor, and thus it is known that the above arrangement can improve the operation performance of the dual two-stage drum rotor type compressor.

In the present embodiment, the first blade 801, the second blade 802, the third blade 803 and the fourth blade 804 can reciprocate; the first piston 521, the second piston 522, the third piston 523, and the fourth piston 524 are all rotationally movable.

Further, the third suction port 5130 is used for introducing the low-temperature and low-pressure refrigerant; the third discharge port 5131 is used to discharge the low-temperature and low-pressure refrigerant compressed in one stage.

The third discharge port 5131 is connected to the fourth suction port 5140 such that the third discharge chamber 5133 communicates with the fourth suction chamber 5142; the fourth suction port 5140 is used for flowing the low-temperature and low-pressure refrigerant compressed in one stage; the fourth discharge port 5141 is configured to discharge the high-temperature and high-pressure refrigerant to the outside of the casing 100 through the second cylinder cover 502 (wherein a discharge through hole communicating with the casing 100 may be disposed on the second cylinder cover 502 to discharge the high-temperature and high-pressure refrigerant to the outside of the casing 100 through the inside of the casing 100). More specifically, the first exhaust port 5111 is configured to discharge a high-temperature and high-pressure refrigerant formed after two-stage compression to the inside of the casing 100 through the first cylinder head 501, the fourth exhaust port 5141 is configured to discharge a high-temperature and high-pressure refrigerant formed after two-stage compression to the inside of the casing 100 through the second cylinder head 502, and the two discharged high-temperature and high-pressure refrigerants can be merged into one high-temperature and high-pressure refrigerant inside the casing 100 and discharged to the outside of the casing 100 through the exhaust pipe 101 disposed at the upper end of the casing 100.

The direction of the low-temperature and low-pressure refrigerant introduced into the second suction port 5120 is opposite to the direction of the low-temperature and low-pressure refrigerant introduced into the third suction port 5130; a direction in which the first suction port 5110 flows in the low-temperature and low-pressure refrigerant compressed in one stage is opposite to a direction in which the fourth suction port 5140 flows in the low-temperature and low-pressure refrigerant compressed in one stage.

In this embodiment, referring to fig. 5a, 5b, 6a and 6b in particular, the opening directions of the first suction port 5110, the second suction port 5120, the third suction port 5130 and the fourth suction port 5140 are sequentially different by 180 °; the opening directions of the first exhaust port 5111, the second exhaust port 5121, the third exhaust port 5131, and the fourth exhaust port 5141 are sequentially different by 180 °.

The direction of the low-temperature and low-pressure refrigerant introduced into the second suction port 5120 is opposite to the direction of the low-temperature and low-pressure refrigerant introduced into the third suction port 5130; the direction of the high temperature and high pressure refrigerant discharged from the first discharge port 5111 is opposite to the direction of the high temperature and high pressure refrigerant discharged from the fourth discharge port 5141.

From this, it can be further understood that when the crankshaft 300 rotates by an angle θ, the first eccentric portion 301 drives the center point of the first piston 521 inside the first cylinder 511 to rotate by an angle θ, and then the center point of the second piston 522 inside the second cylinder 512 rotates by 180 ° + angle θ, the center point of the third piston 523 inside the third cylinder 513 rotates by an angle θ, and the center point of the fourth piston 524 inside the fourth cylinder 514 rotates by 180 ° + angle θ, so that at any time, the volumes of the intake/exhaust chambers of the four cylinders are always consistent, and since the position of the second intake chamber 5122 of the second cylinder 512 is 180 ° different from the position of the third intake chamber 5132 of the third cylinder 513, and the position of the second exhaust chamber 5123 of the second cylinder 512 is 180 ° different from the position of the third exhaust chamber 5133 of the third cylinder 513; the direction of the low-temperature and low-pressure refrigerant introduced into the second suction port 5120 is opposite to the direction of the low-temperature and low-pressure refrigerant introduced into the third suction port 5130; therefore, the acting forces of the two parts on the crankshaft are just equal and opposite, and are mutually offset, namely the resultant gas force on the crankshaft approaches zero or equals zero; similarly, the position and the rotation angle of the first air suction cavity 5112 of the first air cylinder 511 and the position and the rotation angle of the fourth air suction cavity 5142 of the fourth air cylinder 514 are different by 180 degrees, the position and the rotation angle of the first air discharge cavity 5113 of the first air cylinder 511 and the position and the rotation angle of the fourth air discharge cavity 5143 of the fourth air cylinder 514 are different by 180 degrees, the direction of the high-temperature and high-pressure refrigerant discharged by the first air discharge port 5111 is opposite to the direction of the high-temperature and high-pressure refrigerant discharged by the fourth air discharge port 5141, so that the acting force on the crankshaft is just equal and opposite, and is mutually offset, that is, the resultant gas force on the crankshaft is; the stress state of the crankshaft is improved, and the abrasion of the crankshaft is reduced, so that the reliability of the compressor is improved.

With continued reference to fig. 2, the dual two-stage rolling rotor compressor further comprises: at least one liquid separator, preferably, includes a first liquid separator 601 and a second liquid separator 602, the first liquid separator 601 is located at one side of the outside of the case 100 and is connected to the second suction port 5120 for supplying the low-temperature and low-pressure refrigerant to the second cylinder 512. The second dispenser 602 is located at the other side of the outside of the case 100 and connected to the third suction port 5130 to supply the low-temperature and low-pressure refrigerant to the third cylinder 513.

Further, the double two-stage rolling rotor compressor further includes: and a cooling device disposed on a communication path between the first compression sub-unit and the second compression sub-unit and/or a communication path between the third compression sub-unit and the fourth compression sub-unit, wherein the cooling device is configured to cool the low-temperature low-pressure refrigerant, which flows through the communication path and is subjected to the first-stage compression. Specifically, the cooling device includes: a first bend 701 and a second bend 702; the first elbow 701 communicates the first compression subunit and the second compression subunit, cools the low-temperature and low-pressure refrigerant subjected to the first-stage compression by the second compression subunit, and then the cooled low-temperature and low-pressure refrigerant flows into the first compression subunit to be subjected to the second-stage compression; the second elbow 702 communicates the third compression subunit and the fourth compression subunit, cools the low-temperature and low-pressure refrigerant that has undergone the first-stage compression by the third compression subunit, and then the cooled low-temperature and low-pressure refrigerant flows into the fourth compression subunit to undergo the second-stage compression.

In some other embodiments, as shown in fig. 3, 5a and 5b, in particular, the cooling device further includes several coolers disposed on the first elbow 701 and/or the second elbow 702, and the coolers are used for further cooling the low-temperature and low-pressure refrigerant which flows through the communication path and is subjected to the first stage compression. Specifically, a first cooler 710 is disposed on the first elbow 701, and the first cooler 710 is configured to further cool the low-temperature and low-pressure refrigerant that flows through the first elbow 701 and is subjected to the first-stage compression by the second compression sub-unit, and then the cooled low-temperature and low-pressure refrigerant flows into the first compression sub-unit to be subjected to the second-stage compression and is discharged. A second cooler 720 is disposed on the second elbow 702. The second cooler 720 is used for further cooling the low-temperature and low-pressure refrigerant flowing through the second elbow 702 and subjected to the first-stage compression by the third compression sub-unit, and then the cooled low-temperature and low-pressure refrigerant flows into the fourth compression sub-unit to be subjected to the second-stage compression and then is discharged. In this embodiment, the added cooler is used for further cooling the low-temperature low-pressure refrigerant after being compressed by the first stage, so that the temperature of the low-temperature low-pressure refrigerant after being compressed by the first stage is effectively reduced, the suction temperature and the exhaust temperature during the subsequent two-stage compression of the low-temperature low-pressure refrigerant after being compressed by the first stage can be reduced, the compression performance and the volumetric efficiency of the rolling rotor compressor are improved, and the performance of the air conditioning system with the double two-stage rolling rotor compressor is improved. In some other embodiments, the cooling device may also be another component which has the purpose of cooling the low-temperature and low-pressure refrigerant which flows through the communication path and is subjected to the first-stage compression, and the cooler is only one preferred embodiment of the present invention, and the present invention is not limited thereto.

More specifically, the first elbow 701 is used to communicate the second exhaust port 5121 with the first intake port 5110. The second elbow 702 is used to communicate the third air outlet 5131 with the fourth air inlet 5140.

Further, the first intermediate plate 531 is provided with a first air path (not shown) communicating with the second air discharge chamber 5123; one end of the first elbow 701 communicates with the first air path, and the other end of the first elbow 701 communicates with the first suction port 5110.

The third intermediate plate 533 is provided with a second air path (not shown) communicating with the third air discharge chamber 5133; one end of the second elbow 702 is communicated with the second air passage, and the other end of the second elbow 702 is communicated with the fourth suction port 5140. The first bent pipe 701 and the second bent pipe 702 are arranged to communicate the second air discharge chamber 5121 with the first air suction chamber 5110 and the third air discharge chamber 5133 with the fourth air suction chamber 5142, and simultaneously, the low-temperature and low-pressure refrigerant compressed by the second compression unit and the low-temperature and low-pressure refrigerant compressed by the third compressor unit are cooled.

Referring to fig. 2, 3 and 4, the dual two-stage rolling rotor type compressor further includes: a first muffler 401 and a second muffler 402 for reducing noise generated when the high-temperature and high-pressure refrigerant is discharged, the first muffler 401 being disposed on the first cylinder head 501; said second muffler 402 is arranged on said second cylinder head 502.

Further, the double two-stage rolling rotor compressor further includes: set up inside the casing 100 and be located motor 200 above first cylinder cap 501, motor 200 includes: a motor rotor (not shown) and a motor stator (not shown), wherein the motor rotor is sleeved outside one end (upper part) of the crankshaft 300, and the motor stator is sleeved outside the motor rotor; the motor 200 is configured to drive the crankshaft 300 to rotate, and further drive the first piston 521, the second piston 522, the third piston 523, and the fourth piston 524 to rotate, so as to compress the refrigerant.

Further, the high-temperature and high-pressure gas discharged from the first and second two-stage compression units flows through the motor 200 to cool the motor 200.

Referring to fig. 7, fig. 7 is a schematic diagram illustrating a comparison between the magnitude of resultant gas force applied to the crankshaft of a dual two-stage rolling rotor compressor according to an embodiment of the present invention and the crankshaft of a two-stage and single-stage rolling rotor compressor according to the prior art, as a function of the rotation angle of the crankshaft. As can be seen from fig. 7, the resultant gas force experienced by the crankshaft of the dual two-stage rolling rotor compressor provided in this embodiment approaches to zero or is equal to zero, whereas the magnitude of the resultant gas force experienced by the crankshaft of the dual two-stage and single-stage rolling rotor compressors in the prior art changes with the rotation angle of the crankshaft, and the resultant gas force experienced by the crankshaft is distributed in a curve, which leads to the problems of increasing the abrasion of the crankshaft and reducing the reliability of the compressor; the resultant gas force borne by the crankshaft of the double-two-stage rolling rotor compressor provided by the embodiment does not change along with the change of the rotation angle of the crankshaft, the stress state of the crankshaft is improved, and the double-two-stage rolling rotor compressor has the advantages of reducing the abrasion of the crankshaft and improving the reliability of the compressor.

Based on the above embodiment, as shown in fig. 4, the present invention further provides an air conditioning system, including: a condenser 910, a throttle valve 920 and an evaporator 930, which are connected in series, and a double two-stage rolling rotor type compressor as described in the above embodiment; an exhaust pipe on the shell of the double two-stage rolling rotor compressor is communicated with the condenser 910, and the evaporator 930 is respectively communicated with the first liquid separator 601 and the second liquid separator 602 of the double two-stage rolling rotor compressor; the double two-stage rolling rotor compressor is used for compressing the low-temperature low-pressure refrigerant to obtain a high-temperature high-pressure gaseous refrigerant; the condenser 910 is configured to release heat from the high-temperature high-pressure gaseous refrigerant to obtain a high-temperature high-pressure liquid refrigerant; the throttle valve 920 is used for throttling the high-temperature high-pressure liquid refrigerant to obtain a low-temperature low-pressure liquid refrigerant; the evaporator 930 is configured to absorb heat and evaporate the low-temperature and low-pressure liquid refrigerant to obtain the low-temperature and low-pressure gaseous refrigerant, and respectively flow back to the first liquid separator 601 and the second liquid separator 602 for use in a next refrigeration cycle.

Preferably, the process of the double two-stage rolling rotor compressor for compressing the low-temperature low-pressure refrigerant gas to obtain a high-temperature high-pressure refrigerant gas further comprises: the low-temperature and low-pressure gaseous refrigerant in the liquid separator respectively enters a suction port 5120 of the second cylinder 512 of the second compression sub-unit 510 and a suction port 5130 of the third cylinder 513 of the third compression sub-unit 520, and the second compression sub-unit 510 performs primary compression on the low-temperature and low-pressure gaseous refrigerant in the cylinder thereof; the refrigerant after the first-stage compression in the second compression subunit 510 enters the first intermediate plate 531 and the first elbow 701 with the first cooler 710, at this time, since both the temperature and the pressure of the gaseous low-temperature and low-pressure refrigerant after the first-stage compression will be raised, the temperature of the refrigerant will be lowered after the refrigerant is cooled by the first cooler 710 and the first elbow 701, and then the refrigerant enters the first cylinder 511 of the first compression subunit 500 for second-stage compression to obtain a high-temperature and high-pressure gaseous refrigerant, and the high-temperature and high-pressure gaseous refrigerant is discharged from the first cylinder head 501.

The third compression subunit 520 also performs one-stage compression on the low-temperature and low-pressure refrigerant in the cylinder; the refrigerant primarily compressed by the third compression subunit 520 enters the third intermediate plate 533 and the second elbow 702 with the second cooler 720, at this time, since both the temperature and the pressure of the low-temperature and low-pressure gaseous refrigerant primarily compressed will rise, and then the refrigerant is cooled by the second cooler 720 and the second elbow 702, the temperature of the refrigerant will drop, and then the refrigerant enters the fourth cylinder 514 of the fourth compression subunit 530 for secondary compression, so as to obtain a high-temperature and high-pressure gaseous refrigerant, and is discharged from the second cylinder head 502.

The second intermediate plate 532 shown in fig. 4 also serves to separate two-stage compression sub-units, which operate simultaneously.

In summary, the present invention provides a dual two-stage rolling rotor compressor, including: the casing sets up first two-stage compression unit and second two-stage compression unit inside the casing: the first two-stage compression unit comprises a first compression subunit and a second compression subunit which are communicated with each other; the first two-stage compression unit comprises a first compression subunit and a second compression subunit which are communicated with each other; the second two-stage compression unit comprises a third compression sub-unit and a fourth compression sub-unit which are communicated with each other; one compression subunit in the first two-stage compression unit is used as a first-stage compression unit and is used for introducing a low-temperature low-pressure refrigerant and performing first-stage compression on the low-temperature low-pressure refrigerant; the other compression sub-unit in the first two-stage compression unit is used as a second-stage compression unit and is used for carrying out two-stage compression on the low-temperature low-pressure refrigerant after the first-stage compression to obtain a high-temperature high-pressure refrigerant and discharging the high-temperature high-pressure refrigerant; one compression subunit in the second two-stage compression unit is used as a first-stage compression unit and is used for introducing a low-temperature low-pressure refrigerant and performing one-stage compression on the low-temperature low-pressure refrigerant; the other compression sub-unit in the second two-stage compression unit is used as a second-stage compression unit and is used for performing two-stage compression on the low-temperature low-pressure refrigerant subjected to the one-stage compression to obtain a high-temperature high-pressure refrigerant and discharging the high-temperature high-pressure refrigerant; the direction of the low-temperature and low-pressure refrigerant introduced into the first-stage compression unit in the first two-stage compression unit is opposite to the direction of the low-temperature and low-pressure refrigerant introduced into the first-stage compression unit in the second two-stage compression unit; a direction of the low-temperature and low-pressure refrigerant, which is compressed by one stage and flows in from the second-stage compression unit of the first two-stage compression unit, is opposite to a direction of the low-temperature and low-pressure refrigerant, which is compressed by one stage and flows in from the second-stage compression unit of the second two-stage compression unit. The direction of the low-temperature and low-pressure refrigerant introduced into the first-stage compression unit in the first two-stage compression unit is opposite to the direction of the low-temperature and low-pressure refrigerant introduced into the first-stage compression unit in the second two-stage compression unit; the direction of the low-temperature and low-pressure refrigerant which flows into the second-stage compression unit in the first two-stage compression unit and is subjected to one-stage compression is opposite to that of the low-temperature and low-pressure refrigerant which flows into the second-stage compression unit in the second two-stage compression unit and is subjected to one-stage compression, namely the second air suction port, the second air exhaust port, the fourth air suction port and the fourth air exhaust port are constantly kept in the same direction, and the first air suction port, the first air exhaust port, the third air suction port and the third air exhaust port are constantly kept in the same direction, so that the gas resultant force on a crankshaft of the double-two-stage rolling rotor compressor is close to zero or equal to zero, the stress state of the crankshaft is improved, the abrasion of the crankshaft is reduced, and.

The above description is only a preferred embodiment of the present invention, and does not limit the present invention in any way. It will be understood by those skilled in the art that various changes, substitutions and alterations can be made herein without departing from the spirit and scope of the invention as defined by the appended claims.

Claims

1. A dual two-stage rolling rotor compressor comprising: the casing sets up first two-stage compression unit and second two-stage compression unit inside the casing:

2. A dual two-stage rolling rotor compressor as set forth in claim 1, further comprising: and a cooling device disposed on a communication path between the first compression sub-unit and the second compression sub-unit and/or a communication path between the third compression sub-unit and the fourth compression sub-unit, wherein the cooling device is configured to cool the low-temperature low-pressure refrigerant, which flows through the communication path and is subjected to the first-stage compression.

3. A double two-stage rolling rotor type compressor as claimed in claim 2, wherein the first, second, third and fourth compression sub-units are sequentially disposed inside the shell in an axial radial direction of the shell.

4. A dual two-stage rolling rotor compressor as set forth in claim 3, further comprising: the setting is in the inside bent axle of casing to and the interval sets up first eccentric part, second eccentric part, third eccentric part and fourth eccentric part on the bent axle, first eccentric part the second eccentric part the third eccentric part with the eccentric direction of fourth eccentric part differs 180 in proper order.

5. The dual two-stage rolling rotor compressor of claim 4, wherein the first, second, third and fourth eccentric portions are integrally formed with the crankshaft.

6. A compressor of the dual two-stage rolling rotor type according to claim 4, wherein the first compression sub-unit comprises: the device comprises a first cylinder cover, a first cylinder, a first middle plate, a first blade and a first piston, wherein the first blade and the first piston are arranged in the first cylinder; one end of the crankshaft penetrates through the first cylinder cover;

7. A compressor of the dual two-stage rolling rotor type according to claim 6, wherein the second compression sub-unit comprises: the first middle plate, a second cylinder positioned on one side of the first middle plate, which is far away from the first cylinder, a second middle plate, and a second blade and a second piston which are arranged in the second cylinder;

8. A compressor of the double two-stage rolling rotor type according to claim 7,

the third compression subunit includes: the second middle plate, a third cylinder and a third middle plate are positioned on one side of the second middle plate, which is far away from the second cylinder, and a third blade and a third piston are arranged in the third cylinder;

9. A compressor of the double two-stage rolling rotor type according to claim 8,

the fourth compression subunit includes: the third middle plate, a fourth cylinder positioned on one side of the third middle plate, which is far away from the third cylinder, a second cylinder cover, a fourth blade and a fourth piston which are arranged in the fourth cylinder;

the other end of the crankshaft penetrates through the second cylinder cover;

10. A double two-stage rolling rotor compressor as set forth in claim 9, wherein the suction directions of said first suction port, said second suction port, said third suction port and said fourth suction port are sequentially different by 180 °.

11. A dual two-stage rolling rotor compressor as set forth in claim 10, wherein the discharge directions of said first discharge port, said second discharge port, said third discharge port and said fourth discharge port are sequentially different by 180 °.

12. A dual two-stage rolling rotor compressor as set forth in claim 11, further comprising: and the liquid distributors are respectively connected with the second air suction cavity and the third air suction cavity and are used for respectively providing the low-temperature and low-pressure refrigerant for the second air cylinder and the third air cylinder.

13. A dual two-stage rolling rotor compressor as set forth in claim 11 wherein said cooling means further includes: a first bend and a second bend; the first elbow communicates the first compression sub-unit with the second compression sub-unit; the second elbow pipe is communicated with the third compression subunit and the fourth compression subunit; specifically, the first elbow is used for communicating the second exhaust cavity with the first suction cavity; the second elbow is used for communicating the third exhaust cavity with the fourth air suction cavity.

14. A dual two-stage rolling rotor compressor according to claim 11, wherein said cooling means further comprises a plurality of coolers disposed on said first bend and/or said second bend.

15. A double two-stage rolling rotor compressor as set forth in claim 11, wherein said first intermediate plate is provided with a first gas passage communicating with said second discharge chamber; one end of the first elbow is communicated with the first air passage, and the other end of the first elbow is communicated with the first air suction cavity;

16. An air conditioning system, comprising: a condenser, a throttle valve and an evaporator which are communicated in sequence, and a double two-stage rolling rotor compressor as claimed in any one of claims 1 to 15;

the evaporator is used for absorbing heat and evaporating the low-temperature low-pressure liquid refrigerant to obtain the low-temperature low-pressure refrigerant, and the low-temperature low-pressure refrigerant flows back to the liquid separator to be used for the next refrigeration cycle.