CN108533489B - Compressor and air conditioning system - Google Patents

Compressor and air conditioning system Download PDF

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Publication number
CN108533489B
CN108533489B CN201810555836.6A CN201810555836A CN108533489B CN 108533489 B CN108533489 B CN 108533489B CN 201810555836 A CN201810555836 A CN 201810555836A CN 108533489 B CN108533489 B CN 108533489B
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China
Prior art keywords
cylinder
compressor
air
port
discharge
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CN201810555836.6A
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Chinese (zh)
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CN108533489A (en
Inventor
刘星如
郑波
梁祥飞
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Gree Electric Appliances Inc of Zhuhai
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Gree Electric Appliances Inc of Zhuhai
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Priority to CN201810555836.6A priority Critical patent/CN108533489B/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

The application provides a compressor and an air conditioning system. The compressor includes: a first air cylinder and a second air cylinder, wherein a first air suction port, a first air exhaust port and a discharging device positioned between the first air suction port and the first air exhaust port are arranged on the first air cylinder; the second cylinder is provided with a second air suction port and a second air exhaust port, and the discharging device is connected with the second air suction port. Because the first cylinder of the compressor is provided with the discharge device, when the compressor works at a small pressure ratio, part of refrigerant is discharged from the first cylinder of the compressor through the discharge port by the action of the discharge device, and the discharged refrigerant is sucked by the air suction port of the second cylinder. The application effectively improves the operation reliability of the compressor, has simple structure, is convenient to realize, and can also improve the performance of the compressor to a certain extent.

Description

Compressor and air conditioning system
Technical Field
The application relates to the technical field of air conditioners, in particular to a compressor and an air conditioning system.
Background
In recent years, in order to solve the problem of clean heating in northern areas of China, the enthalpy increasing technology has been paid great attention to the capability and energy efficiency improvement at the same time.
At present, a rotor type compressor with an enthalpy increasing function plays an extremely critical role in the field of small heat pump clean heating. In the rotor type compressor with enthalpy increasing function, double-stage enthalpy increasing and double-cylinder enthalpy increasing are performed well, wherein in double-cylinder enthalpy increasing, a large cylinder and a small cylinder are arranged in the compressor, an air suction port of the small cylinder is directly connected with an air supplementing branch, and intermediate pressure in a gas-liquid separator is used as suction pressure. The compressor has simple compression process and avoids the mixing loss of two stages, and has better performance than two stages under the working condition of not large pressure ratio. However, when the system is operated under a small pressure ratio condition, the gas in the gas-liquid separator is less, the small cylinder of the double-cylinder compressor of the type can easily suck a large amount of refrigerant liquid, and the reliability of the compressor is further affected.
To solve this problem, patent No. 201610210434.3 proposes a solution for bypassing a cylinder in a twin-cylinder compressor at high temperature, which can solve the problem of reliability and also has an unloading effect so that the compressor can operate at a higher frequency under a low pressure ratio condition, but the operation mode of the solution is complex and the performance is poor. Similarly, the patent needle with the patent number of 201510760115.5 provides another better scheme, the scheme is provided with a switching device outside the compressor, when the pressure ratio is smaller, the air supplementing branch is closed, the air suction port of the small cylinder is directly connected with the air suction pipeline, and the scheme effectively solves the problem of the reliability of the double-cylinder enthalpy-increasing compressor under the small pressure ratio, but still has a larger improvement space.
Disclosure of Invention
The application mainly aims to provide a compressor and an air conditioning system, which are used for solving the problems of complex structure and low reliability under a small pressure ratio of a double-cylinder enthalpy-increasing compressor in the prior art.
In order to achieve the above object, according to one aspect of the present application, there is provided a compressor comprising: a first air cylinder and a second air cylinder, wherein a first air suction port, a first air exhaust port and a discharging device positioned between the first air suction port and the first air exhaust port are arranged on the first air cylinder; the second cylinder is provided with a second air suction port and a second air exhaust port, and the discharging device is connected with the second air suction port.
Further, the discharging device is arranged on the cylinder wall of the first cylinder or the upper flange or the lower flange and is positioned between the first air suction port and the first air exhaust port; the discharging device comprises a discharging port, a discharging valve and a conveying channel, wherein the discharging valve is arranged as a tongue reed and used for controlling the opening and closing of the discharging port, the discharging valve is arranged at the outer side of the discharging port, and the conveying channel is connected between the outer side of the discharging valve and the second air suction port.
Further, the delivery passage is a pipe connected between the discharge port and the second suction port or a passage formed between the first cylinder and the second cylinder directly inside the compressor.
Further, the transfer passage is provided inside or outside the first cylinder and the second cylinder.
Further, if the suction volume of the first cylinder is V 1 The first rotor of the first cylinder just rotates through the lower edge angle of the first air suction port, and the volume of the compression cavity corresponding to the compression cavity of the first cylinder just seals is V 2 The suction volume of the second cylinder is V 3 The volume of the first cylinder corresponding to the setting position of the discharge port is V 4 Wherein V is 4 The following formula should be satisfied: v (V) 4 ＝V 2 -(0.9～1.2)V 3 。
Further, V 4 The following formula is satisfied: v (V) 4 ＝V 2 -(0.9～1.2)V 3 。
Further, the outlet is round, square, triangular or trapezoidal.
Further, the first exhaust port and the second exhaust port are connected through mutually independent channels.
Further, the compressor further comprises a flange arranged close to the first cylinder, and the discharging device is arranged on the flange.
According to another aspect of the present application, there is provided an air conditioning system including a compressor, the compressor being the compressor described above.
Further, the air conditioning system further comprises a gas-liquid separator, and the gas-liquid separator is communicated with the second air suction port of the compressor through a connecting pipeline.
Further, a control valve is arranged on the connecting pipeline.
Further, the control valve is a throttle valve or a stop valve.
Further, the air conditioning system further comprises a first heat exchanger, a second heat exchanger, a first throttle valve and a second throttle valve, wherein the first heat exchanger is connected with the first exhaust port and the second exhaust port, the first throttle valve is connected between the gas-liquid separator and the first heat exchanger, and the second throttle valve and the second heat exchanger are sequentially connected between the gas-liquid separator and the first air suction port.
Further, the air conditioning system is provided with an unloading operation mode and a double-cylinder enthalpy increasing mode, when the air conditioning system is in the unloading operation mode, a control valve of the compressor is in a closed state, and a discharge valve of the compressor is in an open state; when the air conditioning system is in the double-cylinder enthalpy increasing mode, the control valve of the compressor is in an opening state, and the discharge valve of the compressor is in a closing state.
By applying the technical scheme of the application, as the first cylinder of the compressor is provided with the discharge device, when the compressor works at a small pressure ratio, part of refrigerant is discharged from the first cylinder of the compressor through the discharge port by the action of the discharge device, and the discharged refrigerant is sucked by the air suction port of the second cylinder. Therefore, the problem of air suction of the second cylinder after the enthalpy increasing pipeline connected with the second cylinder is cut off under the working condition of small pressure ratio is effectively solved, and meanwhile, the partial volume of the first cylinder of the compressor can be unloaded to a certain extent, so that the running frequency of the compressor under partial load is higher. Overall, the proposed solution effectively improves the operational reliability of the compressor, and has a simple structure, convenient implementation and at the same time, it also improves the performance of the compressor to a certain extent.
Drawings
The accompanying drawings, which are included to provide a further understanding of the application and are incorporated in and constitute a part of this specification, illustrate embodiments of the application and together with the description serve to explain the application. In the drawings:
fig. 1 schematically illustrates a connection relationship diagram of an air conditioning system of the present application;
fig. 2 schematically shows an enlarged view of a compressor section of the present application;
FIG. 3 schematically illustrates a flow chart of a refrigerant when the air conditioning system of the present application is in a dual-cylinder enthalpy increasing mode; and
fig. 4 schematically shows a flow diagram of the refrigerant when the air conditioning system of the present application is in an unloaded mode of operation.
Wherein the above figures include the following reference numerals:
1. a compressor; 11. a first cylinder; 111. a first air suction port; 112. a first exhaust port; 114. a first rotor; 115. a first slide; 116. discharging the device; 12. a second cylinder; 121. a second air suction port; 122. a second exhaust port; 124. a second rotor; 125. a second slide; 2. a first heat exchanger; 3. a second heat exchanger; 4. a first throttle valve; 5. a gas-liquid separator; 6. a control valve; 7. and a second throttle valve.
Detailed Description
It should be noted that, without conflict, the embodiments of the present application and features of the embodiments may be combined with each other. The application will be described in detail below with reference to the drawings in connection with embodiments.
It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of exemplary embodiments according to the present application. As used herein, the singular is also intended to include the plural unless the context clearly indicates otherwise, and furthermore, it is to be understood that the terms "comprises" and/or "comprising" when used in this specification are taken to specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof.
It should be noted that the terms "first," "second," and the like in the description and the claims of the present application and the above figures are used for distinguishing between similar objects and not necessarily for describing a particular sequential or chronological order. It is to be understood that the data so used may be interchanged where appropriate such that embodiments of the application described herein may be capable of being practiced otherwise than as specifically illustrated and described. Furthermore, the terms "comprises," "comprising," and "having," and any variations thereof, are intended to cover a non-exclusive inclusion, such that a process, method, system, article, or apparatus that comprises a list of steps or elements is not necessarily limited to those steps or elements expressly listed but may include other steps or elements not expressly listed or inherent to such process, method, article, or apparatus.
Spatially relative terms, such as "above … …," "above … …," "upper surface at … …," "above," and the like, may be used herein for ease of description to describe one device or feature's spatial location relative to another device or feature as illustrated in the figures. It will be understood that the spatially relative terms are intended to encompass different orientations in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, elements described as "above" or "over" other devices or structures would then be oriented "below" or "beneath" the other devices or structures. Thus, the exemplary term "above … …" may include both orientations of "above … …" and "below … …". The device may also be positioned in other different ways (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.
Referring to fig. 1 to 4, according to an embodiment of the present application, there is provided a compressor 1, where the compressor 1 is preferably a double-cylinder enthalpy-increasing compressor, where the double-cylinder enthalpy-increasing compressor means that the compressor has two cylinders, different from two stages, each of which independently sucks air, and there is no device for connecting low-pressure-stage exhaust air with high-pressure-stage suction air, and exhaust air of both cylinders is directly discharged; the air suction port of one cylinder body is connected with the outlet of the evaporator, and the air suction port of the other cylinder body is connected with the outlet of the gas-liquid separator.
Specifically, the compressor 1 in the present embodiment includes a first cylinder 11 and a second cylinder 12, wherein the first cylinder 11 is provided with a first suction port 111, a first discharge port 112, and a discharge device 116 located between the first suction port 111 and the first discharge port 112; the second cylinder 12 is provided with a second intake port 121 and a second exhaust port 122, and the discharge device 116 communicates with the second intake port 121.
Since the discharge device 116 is disposed on the first cylinder 11 of the compressor 1 in this embodiment, when the compressor 1 works at a small pressure ratio, the refrigerant in the first cylinder 11 can be directly output into the second cylinder 12 through the effect of the discharge device 116, which can unload part of the cylinders of the compressor 1 to a certain extent, so that the operation frequency of the compressor 1 under part load is higher, the performance of the compressor is improved to a certain extent, the operation reliability of the compressor 1 is improved, and the structure is simple and convenient to implement.
In a preferred embodiment of the application, as shown in connection with fig. 2, the bleeder 116 in this embodiment is provided in the cylinder wall of the first cylinder 11 between the first suction port 111 and the first exhaust port 112. Specifically, the discharging device 116 in the present embodiment includes a discharging port (not shown in the figure), a discharging valve (not shown in the figure) provided as a tongue piece for controlling opening and closing of the discharging port, and a delivery passage (not shown in the figure) connected between the outside of the discharging valve and the second suction port 121. The discharge device 116 facilitates the control of the on-off of the delivery passage at a proper timing, thereby enabling the compressor 1 to be reliably operated with a small pressure ratio.
Of course, the intermediate compressor 1 according to the application comprises a flange arranged close to the first cylinder 11, on which flange the tapping device 116 can be arranged during the actual arrangement of the tapping device 116, wherein the flange can be an upper flange or a lower flange, in particular depending on the mounting position of the first cylinder 11.
In a preferred embodiment of the application the delivery channel is a conduit connected between the discharge opening and the second suction opening 121, although in other embodiments of the application the delivery channel can also be arranged to work a channel formed between the first cylinder 11 and the second cylinder 12 directly inside the compressor.
In carrying out the installation, the transfer passage may be provided inside or outside the first cylinder 11 and the second cylinder 12.
The compressor 1 in this embodiment further includes a crankshaft (not shown in the drawings), a first rotor 114, a first sliding vane 115, a second rotor 124, and a second sliding vane 125, where the first rotor 114 and the second rotor 124 are both sleeved on the crankshaft, the first sliding vane 115 is disposed in the first cylinder 11 and is in driving connection with the first rotor 114, and the second sliding vane 125 is disposed in the second cylinder 12 and is in driving connection with the second rotor 124. When the crankshaft rotates, the first rotor 114 and the second rotor 124 are driven to drive the first sliding vane 115 and the second sliding vane 125 to move respectively, so that the refrigerants in the first cylinder 11 and the second cylinder 12 are conveniently compressed. In actually setting the pressure relief outlet bit setting in this embodiment, the following should be considered:
from the position that the first rotor 114 of the first cylinder 11 of the compressor 1 just rotates to the lower edge angle of the first air suction port 111 (namely, the compression cavity just forms), the reduced volume of the compression cavity just equals to the rotation angle corresponding to the suction volume of the second cylinder 12, and the cylinder wall and flange positions corresponding to the rotation angle are standard reference points of the setting positions of the discharge ports; when the discharge port position is set at the standard reference point, the discharge valve is opened before the first rotor 114 rotates past the standard reference point, the refrigerant in the first cylinder 11 of the compressor 1 is discharged through the discharge port, and when the first rotor 114 rotates past the standard reference point, the discharge port is closed until the first cylinder 11 is opened again for the next cycle; since the bleed volume is exactly equal to the suction volume of the second cylinder 12 (irrespective of the volumetric efficiency of the second cylinder 12), the suction pressure of the second cylinder 12 will be exactly equal to the suction pressure of the first cylinder 11, this position being the most efficient, with the least losses, being the preferred position for the bleed; if the position of the discharge outlet is in front of the standard reference point, the suction pressure of the second cylinder is smaller than that of the first cylinder 11, and the loss is larger; similarly, if the position of the discharge port is designed to be behind the standard reference point, the suction pressure of the second cylinder 12 will be greater than the suction pressure of the first cylinder 11, that is, after waiting for the first cylinder 11 to compress for a period of time, the discharge port will be opened again, and since the discharge device 116 will bring a certain clearance volume, the higher the discharge pressure, the greater the loss, so after the design is at the special position, a certain loss will be brought;
however, in practice, the volumetric efficiency of the second cylinder 12 of the compressor 1 must be considered, and there is a certain resistance of the discharge valve, and if the discharge port position is actually set at the position corresponding to the standard reference point, the pressure in the suction pipe of the second cylinder 12 will fluctuate due to the difference in suction angles of the first cylinder 11 and the second cylinder 12, so that the discharge port position is limited according to the practical situation, specifically as follows:
if the suction volume of the first cylinder 11 of the compressor is assumed to be V 1 The first rotor 114 of the first cylinder 11 just rotates over the lower edge angle of the first suction port 111 and the compression chamber of the first cylinder 11 just seals with a corresponding compression chamber volume V 2 The suction volume of the second cylinder 12 is V 3 The volume of the first cylinder 11 corresponding to the position of the discharge port is V 4 Wherein V is 4 The following formula should be satisfied: v (V) 4 ＝V 2 -(0.9～1.2)V 3 . Therefore, the refrigerant which is not compressed by the first cylinder 11 can be directly introduced into the second cylinder 12 as much as possible, the second cylinder 12 can be ensured to suck enough refrigerant as much as possible for compression, the working efficiency and the operation reliability of the compressor are further improved, the structure is simple, and the realization is convenient.
Preferably, consider V 2 And V is equal to 1 Closer, V 4 The following formula should be satisfied: v (V) 4 ＝V 1 -(0.85～1.25)V 3 。
Preferably, the outlet in this embodiment may be provided in a circular shape, or may be provided in a square shape, a triangular shape, a trapezoid shape, or other regular or irregular shapes, so long as other modifications are within the scope of the present application.
The first exhaust port 112 and the second exhaust port 122 in the present embodiment are connected to the outside of the compressor 1 through mutually independent passages, unlike a two-stage compressor, the working efficiency of the compressor in the present embodiment can be improved.
Preferably, the first cylinder 11 and the second cylinder 12 in this embodiment are any combination of rotor form, piston form and vortex form, so as to be convenient for designing according to the specific use condition of the air conditioning system. According to another aspect of the present application, there is provided an air conditioning system including a compressor 1, the compressor 1 being the compressor 1 in the above-described embodiment.
Preferably, the air conditioning system in the present embodiment further includes a gas-liquid separator 5, and the gas-liquid separator 5 communicates with the second suction port 121 through a connection pipe. More preferably, the connecting pipe in the present embodiment is provided with a control valve 6, and the operation of the compressor 1 is controlled by the control valve 6.
The control valve 6 in the present embodiment is a throttle valve or a stop valve, however, in other embodiments of the present application, the control valve 6 may be another on-off valve, and any other modification forms within the concept of the present application are within the scope of the present application.
In design, the volume ratio of the first cylinder 11 and the second cylinder 12 of the double-cylinder enthalpy-increasing compressor in the embodiment can be designed according to actual requirements, and the position of the discharging device and the intermediate pressure under different working conditions can be determined by determining the volume ratio.
As shown in fig. 1 to 4 again, the air conditioning system in the present embodiment further includes a first heat exchanger 2, a second heat exchanger 3, a first throttle valve 4, and a second throttle valve 7, wherein the first heat exchanger 2 is connected to the first exhaust port 112 and the second exhaust port 122, the first throttle valve 4 is connected between the gas-liquid separator 5 and the first heat exchanger 2, and the second throttle valve 7 and the second heat exchanger 3 are sequentially connected between the gas-liquid separator 5 and the first air intake port 111.
When the air conditioning system is in the unloading operation mode, the control valve 6 is in a closed state, and the discharge valve of the compressor 1 is in an open state. At this time, when the air conditioning system operates under the working condition of small pressure ratio and the gas amount in the gas-liquid separator 5 is small, the air conditioning system is unloaded and operated, and the specific implementation scheme is as follows: the control valve 6 is closed, the high-temperature high-pressure gaseous refrigerant is changed into high-pressure supercooled liquid refrigerant through the first heat exchanger 2, then enters the gas-liquid separator 5 through the first throttle valve 4 and is changed into medium-pressure refrigerant, all the refrigerant in the gas-liquid separator 5 is changed into low-pressure two-phase refrigerant through the second throttle valve 7 by closing the control valve 6, and enters the second heat exchanger 3, and the low-pressure two-phase refrigerant is sucked into the first air suction port 111 of the first air cylinder 11 of the compressor 1 after the second heat exchanger 3 is evaporated; since the control valve 6 is closed at this time, the back pressure of the second cylinder 12 of the compressor 1 will rapidly decrease with time, and when the back pressure decreases to a pressure higher than the pressure at which the first rotor 114 in the compression chamber of the first cylinder 11 turns to the corresponding position, the discharge valve is opened, and the refrigerant in the first cylinder 11 is discharged to the second suction port 121 of the second cylinder 12; in this operating mode, the steady suction pressure of the second cylinder 12 is determined jointly by the volume of the second cylinder 12, the frequency of the compressor 1 and the discharge position.
When the air conditioning system is in the double-cylinder enthalpy increasing mode, the control valve 6 is in an open state, and the discharge valve of the compressor 1 is in a closed state. Specifically, the refrigerant is discharged from the first cylinder 11 and the second cylinder 12 of the compressor 1, is changed into high-pressure supercooled liquid through the first heat exchanger 2, and enters the gas-liquid separator 5 through the first throttle valve 4; the refrigerant in the gas-liquid separator 5 is divided into two paths, wherein the bottom refrigerant liquid enters the second throttle valve 7 through the second outlet of the gas-liquid separator 5 to be throttled into low-pressure two-phase refrigerant which enters the inlet of the second heat exchanger 3, the low-pressure two-phase refrigerant is evaporated in the second heat exchanger 3 to be changed into gaseous refrigerant, and the gaseous refrigerant is sucked by the first air suction port 111 of the first cylinder 11; the other path of refrigerant gas in the gas-liquid separator 5 flows out through the first outlet of the gas-liquid separator 5 and is sucked in through the control valve 6 by the second air suction port 121 of the second cylinder 12 of the compressor 1; in this case, the back pressure of the discharge device 116 is the pressure in the gas-liquid separator 5, and since the discharge device 116 is provided at the position where the rotation angle of the first cylinder 11 of the compressor 1 is small, when the first rotor 114 rotates to the discharge device 116 position, the pressure in the compression chamber is lower than the intermediate pressure in the gas-liquid separator 5, and therefore in this case, the discharge valve is closed, and the air conditioning system is in the parallel compression mode.
From the above description, it can be seen that the above embodiments of the present application achieve the following technical effects:
the application provides the double-cylinder compressor capable of efficiently operating under the working conditions of large pressure ratio and small pressure ratio by utilizing the parallel compression technology and the refrigerant discharge technology, the double-cylinder compressor better solves the reliability problem of the double-cylinder compressor of parallel compression under the working condition of small pressure ratio, and simultaneously, partial cylinders of the compressor are unloaded to a certain extent under the working condition of small pressure ratio, so that the operating frequency of the compressor under partial load is higher, and the performance of the compressor under the partial working condition is improved to a certain extent.
The above description is only of the preferred embodiments of the present application and is not intended to limit the present application, but various modifications and variations can be made to the present application by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application should be included in the protection scope of the present application.

Claims (14)

1. A compressor (1), characterized by comprising:
a first cylinder (11) and a second cylinder (12), wherein,
the first cylinder (11) is provided with a first air suction port (111), a first air exhaust port (112) and a discharge device (116) positioned between the first air suction port (111) and the first air exhaust port (112);
the second air cylinder (12) is provided with a second air suction port (121) and a second air exhaust port (122), and the discharging device (116) is connected with the second air suction port (121);
if the suction volume of the first cylinder (11) is V 1 The first rotor (114) of the first cylinder (11) just rotates through the lower edge angle of the first air suction port (111), and the volume of the compression cavity corresponding to the compression cavity of the first cylinder (11) just seals is V 2 The suction volume of the second cylinder (12) is V 3 The discharge device (116) comprises a discharge port, and the volume of the first cylinder (11) corresponding to the position of the discharge port is V 4 Wherein V is 4 The following formula is satisfied:
。
2. compressor (1) according to claim 1, characterized in that said discharge means (116) are provided on the cylinder wall or on the upper flange or on the lower flange of said first cylinder (11) and are located between said first suction opening (111) and said first discharge opening (112);
the discharging device (116) further comprises a discharging valve and a conveying channel, wherein the discharging valve is arranged as a tongue reed and used for controlling the opening and closing of the discharging port, the discharging valve is arranged at the outer side of the discharging port, and the conveying channel is connected between the outer side of the discharging valve and the second air suction port (121).
3. The compressor (1) according to claim 2, characterized in that the delivery channel is a duct connected between the discharge opening and the second suction opening (121) or a channel formed directly inside the compressor between the first cylinder (11) and the second cylinder (12).
4. Compressor (1) according to claim 2, characterized in that the delivery channel is provided inside or outside the first cylinder (11) and the second cylinder (12).
5. Compressor (1) according to claim 1, characterized in that,V 4 the following formula is satisfied:
。
6. compressor (1) according to claim 2, characterized in that said discharge opening is circular or square or triangular or trapezoidal.
7. The compressor (1) of claim 1, wherein the first discharge port (112) and the second discharge port (122) are connected by mutually independent channels.
8. The compressor according to any one of claims 1 to 7, wherein the first cylinder (11) and the second cylinder (12) are in any combination of rotor form, piston form and swirl form.
9. An air conditioning system comprising a compressor (1), characterized in that the compressor (1) is a compressor (1) according to any one of claims 1 to 8.
10. An air conditioning system according to claim 9, characterized in that the air conditioning system further comprises a gas-liquid separator (5), the gas-liquid separator (5) being in communication with the second suction opening (121) of the compressor (1) through a connecting duct.
11. An air conditioning system according to claim 10, characterized in that the connecting duct is provided with a control valve (6).
12. An air conditioning system according to claim 11, characterized in that the control valve (6) is a throttle valve or a shut-off valve.
13. The air conditioning system according to claim 10, further comprising a first heat exchanger (2), a second heat exchanger (3), a first throttle valve (4) and a second throttle valve (7), wherein the first heat exchanger (2) is connected with the first exhaust port (112) and the second exhaust port (122), the first throttle valve (4) is connected between the gas-liquid separator (5) and the first heat exchanger (2), and the second throttle valve (7) and the second heat exchanger (3) are connected in sequence between the gas-liquid separator (5) and the first suction port (111).
14. Air conditioning system according to claim 13, characterized in that it has an unloading operating mode and a double-cylinder enthalpy increasing mode, when the air conditioning system is in the unloading operating mode, the control valve (6) of the compressor (1) is in a closed state, the discharge valve of the compressor (1) is in an open state; when the air conditioning system is in the double-cylinder enthalpy increasing mode, a control valve (6) of the compressor (1) is in an open state, and a discharge valve of the compressor (1) is in a closed state.
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Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105782038A (en) * 2014-12-25 2016-07-20 珠海格力节能环保制冷技术研究中心有限公司 Rotary compressor assembly and air conditioner with same
CN208311044U (en) * 2018-06-01 2019-01-01 珠海格力电器股份有限公司 compressor and air conditioning system

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101691864B (en) * 2009-09-30 2011-08-24 马丽莉 Spherical expansion compressor capable of adapting to variable working conditions

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105782038A (en) * 2014-12-25 2016-07-20 珠海格力节能环保制冷技术研究中心有限公司 Rotary compressor assembly and air conditioner with same
CN208311044U (en) * 2018-06-01 2019-01-01 珠海格力电器股份有限公司 compressor and air conditioning system

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