WO2008101387A1 - A controlling method of a rotary compressor - Google Patents

A controlling method of a rotary compressor Download PDF

Info

Publication number
WO2008101387A1
WO2008101387A1 PCT/CN2008/000225 CN2008000225W WO2008101387A1 WO 2008101387 A1 WO2008101387 A1 WO 2008101387A1 CN 2008000225 W CN2008000225 W CN 2008000225W WO 2008101387 A1 WO2008101387 A1 WO 2008101387A1
Authority
WO
WIPO (PCT)
Prior art keywords
mode
cylinder
compressor
control method
switched
Prior art date
Application number
PCT/CN2008/000225
Other languages
French (fr)
Chinese (zh)
Inventor
Qiang Gao
Zhengxiong Xiaojin
Huaming Li
Duogeng Wu
Original Assignee
Guang Dong Mei Zhi Refrigeration Equipment Co., Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Guang Dong Mei Zhi Refrigeration Equipment Co., Ltd filed Critical Guang Dong Mei Zhi Refrigeration Equipment Co., Ltd
Publication of WO2008101387A1 publication Critical patent/WO2008101387A1/en

Links

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
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0827—Vane tracking; control therefor by mechanical means
    • F01C21/0845—Vane tracking; control therefor by mechanical means comprising elastic means, e.g. springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid
    • 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
    • F04C18/3564—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 the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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

Definitions

  • the present invention relates to a control method for a rotary compressor, and more particularly to a method for controlling the refrigeration capacity of a two-cylinder rotary compressor.
  • variable frequency technology to control rotary compressors with variable frequency function to control the change of the pressure of the freezer compartment is very mature and has been commercialized, mainly by controlling the rotational speed of the rotary compressor at about 15 Hz (equivalent This is achieved by a change between 25% of the displacement and about 120 Hz (equivalent to 200% of the displacement).
  • This capacity control is a capacity control technique that controls the freezing capacity by fixing or unshelving the slide in the cylinder slide groove to change the total amount of cylinder displacement.
  • the frequency conversion technology controls the freezing capacity by changing the speed of the compressor, so the control method is relatively simple.
  • capacity control technology can change the refrigeration capacity in a combination of compression and non-compression in one or two cylinders, and its control techniques and calculations are very important.
  • the technology provided here is a capacity-controlled two-cylinder rotary compressor, not only related to the refrigeration capacity control method, but also related to the minimum refrigeration capacity reduction control technology as a subject.
  • the technical problem to be solved by the present invention is to provide a control method for a low-capacity rotary compressor that further reduces the minimum refrigeration capacity based on the capacity-controlled rotary compressor, and compresses two or more cylinders in the compressor. Independently compressed or uncompressed to overcome the deficiencies in the prior art.
  • the technical solution for solving the above technical problem is: a control method of a rotary compressor, wherein two or more cylinders of different volumes are disposed in the compressor, and each cylinder is provided with a piston and an eccentricity for driving the piston a crankshaft and the eccentric crankshaft bearing support, is provided with a slide groove has a slide spring of the cylinder at least to the cylinder: compressed and uncompressed size switching manner, the compression cylinder operating mode referred to as a cylinder running denoted uncompressed In mode 2, a valve device is disposed outside the compressor, and the valve device uses the high pressure and low pressure generated when the compressor starts to operate to switch the cylinder chamber pressure between the low pressure and the high pressure, and the compressor adopts the following seven times during the entire running time.
  • One or more of the operating methods are operated separately or in combination, wherein the high volume cylinder is the first cylinder, The low volume cylinder is the second cylinder, then:
  • the first cylinder is fixed to mode one, the second cylinder is switched back and forth between mode one and mode two; b) the first cylinder is switched back and forth between mode one and mode two, and the second cylinder is fixed to mode one; c) The first cylinder and the second cylinder are switched between mode one and mode two, respectively;
  • the first cylinder switches back and forth between mode one and mode two, the second cylinder is fixed to mode two; e) the first cylinder is fixed to mode two, and the second cylinder is switched back and forth between mode one and mode two; f) The first cylinder is switched between mode one mode and mode three, the second cylinder is fixed to mode two; g) the first cylinder is fixed to mode two, and the second cylinder is switched by mode one mode and mode three; wherein, the compressor is stopped, In the first mode, the running cylinder is switched to the mode 2 and then stopped. At this time, the power is turned off, then the compressor is started, and the cylinder is kept in the mode 2 state. At this time, the power is turned on, and then the compressor is running stably, then The process of switching to mode one is mode three.
  • the control method provided by the invention can fix the compressor refrigeration capacity under the condition that the motor efficiency is the maximum speed to further improve the compressor efficiency, and the compressor itself does not stop during the control process, and does not consume the compressor start and Excessive power required after start-up prevents inefficiency and prevents vibrations generated during start or stop. It also prevents loads generated during start-up, such as liquid refrigerant suction or oil level, without affecting the compressor. reliability.
  • the compressor using the control method can increase the total running time of mode 2 by a certain period of time T c , and the refrigeration capacity provided by the compressor can be close to 0%, and these advantages are the former inverter compressor and the former two. Not available in the cylinder type capacity control method.
  • FIG. 1 is a schematic structural view of an embodiment of the present invention.
  • FIG. 2 is a cross-sectional structural view of a two-cylinder rotary compressor.
  • Figure 3 shows the calculation of the refrigeration capacity of the two cylinders.
  • 1 is the compressor
  • 2 is the accumulator
  • 3 is the exhaust pipe
  • 4 is the condenser
  • 5 is the automatic expansion valve
  • 6 is the evaporator
  • 7 is the check valve
  • 8 is the valve device
  • 10 is the compression
  • 11 is the motor assembly
  • 12 is the first cylinder
  • 13 is the second cylinder
  • 14.1 is the first piston
  • 14.2 is the second piston
  • 15.1 is the first sliding vane
  • 15.2 is the second sliding vane
  • 16.1 is the first a sliding piece
  • 16.2 is the second sliding piece
  • 17 is the eccentric crankshaft main shaft
  • 18.1 is the upper bearing
  • 18, 2 is the lower bearing
  • 19 is the eccentric crankshaft countershaft
  • 20.1 is the first sliding vane chamber
  • 20.2 is the second sliding vane Room
  • 21 is the first pressure switching tube
  • 22 is the second pressure switching tube
  • 23 is the low pressure tube
  • 24 is the high pressure tube
  • 33 is the intermediate partition.
  • a schematic diagram of a refrigerating cycle of a rotary compressor using the present control method the rotary compressor 1 compresses the low-pressure gas sucked from the accumulator 2, and compresses and discharges the high-pressure gas through the exhaust pipe 3. Thereafter, the liquid refrigerant condensed in the condenser 4 is depressurized by the automatic expansion valve 5, evaporated in the evaporator 6, and the low-pressure refrigerant is returned to the accumulator 2, and is again sucked into the compressor 1 for compression.
  • the check valve 7 installed between the evaporator 6 and the accumulator 2 will be used as a high and low differential pressure maintaining device to be described later.
  • the valve device 8 is disposed outside the compressor 1.
  • the valve device can control the two cylinders to independently perform cylinder compression or stop during the operation of the compressor, so as to realize the phased switching of the compressor refrigeration capacity, so the design of the two cylinder displacements is different.
  • the rotary compressor with capacity control has the same function as the variable-capacity rotary compressor, or it has further capability control.
  • FIG. 2 it is a schematic structural view of the internal structure of a two-cylinder rotary compressor.
  • a compression assembly 10 and a motor assembly 11 are mounted inside the sealed casing of the rotary compressor 1.
  • the compression assembly 10 includes a first cylinder 12 and a second cylinder 13; a first piston 14.1 is disposed in the first cylinder 12, and a first slide 16.1 is mounted in the first vane slot 15.1 of the first cylinder 12, and the second cylinder 13 is mounted.
  • a second piston 14, 2 is disposed therein, and a second sliding plate 16.2 is mounted in the second sliding groove 15.2 of the second cylinder 13;
  • An eccentric crankshaft 17 that drives the first piston 14.1 and the second piston 14.2 supports the upper bearing 18.1 and the lower bearing 18.2 of the eccentric crankshaft 17.
  • the eccentric crankshaft 17 is driven by the motor assembly 11, operates at a certain speed (60 or 50 Hz), and transmits torque to the piston.
  • the first sliding chamber 20.1 of the first cylinder 12 is in contact with the first pressure switching tube 21, and the second sliding chamber 20.2 of the second cylinder 13 is connected to the second pressure switching tube 22, and one end of each switching tube is connected to the valve.
  • the device 8 is connected.
  • One end of the low pressure pipe 23 of the connection valve device 8 is in contact with a low pressure portion such as a suction pipe of the compressor 1, and the high pressure pipe 24 inside the casing of the connection valve device 8 is in contact with the inside of the casing of the compressor 1.
  • the valve unit 8 uses the high pressure and low pressure generated when the compressor starts operating, so that the vane chamber pressures of the first cylinder 12 and the second cylinder 13 are switched between low pressure and high pressure. Therefore, both cylinders can accommodate the fixed slide to stop the compression, that is, mode two, and release the slide to start the compression, that is, mode one. Further, the valve device 8 has a function of making each cylinder mode independent and switching to each other.
  • the compressor is divided into three ranges according to the refrigeration capacity of the compressor, which are 100 ⁇ 65% high range, 65 ⁇ 35% medium range and 35 ⁇ 0% low range.
  • the displacement of the two-cylinder rotary compressor is 100% (such as 40cc), and the respective displacements are: the first cylinder accounts for 65% (ie 26cc) and the second cylinder accounts for 35% (ie 14cc).
  • the control calculation method of the compressor refrigeration capacity will be specifically described. Among them, within a certain time range, the refrigeration capacity provided by the compressor is the sum of the refrigeration capacity provided by the two cylinders respectively.
  • the first is the control method.
  • T C the first cylinder is fixed to mode one operation, and the second cylinder is switched back and forth between mode one and mode two.
  • the total running time of mode one in the first cylinder or the second cylinder is respectively recorded as TAI and T B1 , and T A1 /T C or T B1 /T C is the respective running time ratio.
  • TAI time
  • T B1 time
  • T A1 /T C or T B1 /T C is the respective running time ratio.
  • T A1 /Tc 10
  • the control method b is basically the same as the control method a, except that the first cylinder is switched back and forth between mode one and mode two, and the second cylinder is fixed to mode one operation, so the calculation process is the same as the control method and is not repeated.
  • the external refrigeration capacity of the compressor is 35+65xT A1 /T c .
  • the compressor provides a refrigeration capacity of 65xT A1 /T c +35xT B1 /T c .
  • the first cylinder is switched back and forth between mode one and mode two, the second cylinder is fixed to mode two, and the second cylinder has a freezing capacity of 0. Therefore, the externally provided refrigeration capacity of the compressor is 65 x T A1 /T c .
  • the first cylinder intermittently repeats the compression and non-compression operations.
  • the control method e is opposite to the control method d.
  • the control method e is fixed to the mode 2 by the first cylinder, and the second cylinder is switched back and forth between the mode 1 and the mode 2, and the freezing capacity of the first cylinder is 0, therefore, the compression
  • the external refrigeration capacity provided by the machine is 35xTBl/TC.
  • the second cylinder intermittently repeats the compression and non-compression operations.
  • control method d The advantages of the control method d and the control method e will be specifically described below.
  • the refrigeration capacity provided by the compressor can be reduced to less than 35%.
  • the total running time of mode 2 is appropriately extended.
  • the externally provided refrigeration capacity of the compressor can be close to 0%, and these advantages are the previous inverter compressor and the previous two cylinders. Not available in the volume control method.
  • the mode switching of the cylinder is quite easy, does not consume the excess power required after the compressor is started and started, prevents inefficiency, and prevents vibration generated during starting or stopping. It also prevents the load generated during start-up (such as liquid refrigerant suction or low oil level) without affecting the reliability of the compressor.
  • control method f and the control method g either of the first cylinder (65%) or the second cylinder (35%) of the two methods are fixed to mode two, that is, non-compression operation, and the other mode is mode one.
  • Run and mode three switch. Among them, the compressor is stopped, the first mode is to switch the running cylinder to the second mode, then the power is turned off, then the compressor starts, the cylinder is kept in the mode 2 state, then the power is turned on, then, the compression After the machine runs at an accelerated speed (usually about 1 second), the process of switching to mode one is mode three.
  • the control method g can use the second cylinder (35%) with a smaller displacement, so that the externally provided refrigeration capacity can be controlled more accurately and easily than the control method f. That is to say, the second cylinder with a relatively small displacement is used in the capacity control of less than 35%, which is advantageous in the fine adjustment of the refrigeration capacity control and the startup of the compressor.
  • the second cylinder displacement is less than 35% of the low-range capacity control, it is recommended to use the first cylinder with the larger displacement as the mode 2 and the smaller second cylinder as the mode 1 and mode 2 or mode 3 for the capacity control. .
  • control processes f and g are used to control the compressor shutdown and start, the second cylinder with a small displacement must be switched to mode two beforehand.
  • the control process of the second cylinder is mode one ⁇ mode two mode three ⁇ mode two start mode one.
  • switching The number of times is related to the variation of the compressor's refrigeration capacity, and needs to be optimized through a specific system.
  • the present invention can also achieve different compressor refrigeration capacities by combining different control methods within a certain time range.
  • the specific mode 1 and mode 2 run time settings it is also necessary to design according to the specific system.
  • the automatic expansion valve 5 when the second cylinder is in mode two operation or when the compressor is stopped, the automatic expansion valve 5 is fully closed, which can effectively prevent the condenser (high pressure side) from the evaporator (low pressure side). Gas loss. Moreover, the gas leaking from the compressor casing (high pressure side) to the evaporator (low pressure side) can also be blocked by the check valve 7. That is, the operation time of the mode 2 or the compressor stop time can be extended, and the control is relatively easy.
  • the pressure difference maintaining means can shorten the transition time required for the system to reach the set condition after the compressor starts to be compressed, so that the transition time of the air conditioning system can be shortened and the efficiency can be improved.
  • the check valve can prevent the reverse flow of the high pressure gas generated from the compressor casing to the evaporator after the compression of the compressor is stopped.
  • the pressure difference maintaining device should have many different methods and different structures. Here, only the automatic expansion valve and the check valve are represented, for example, the simple application of the check valve action causes condensation. The circuit between the evaporator and the evaporator is automatically turned off.
  • the control method of the present invention can greatly improve the working efficiency of the compressor and expand the control range of the refrigeration capacity of the compressor. For example, when the compressor speed is fixed at 15 Hz, if the control method d or e is used, the external cooling capacity of the compressor can be made smaller, and the compressor efficiency and air conditioning accuracy can be improved.
  • the subject of frequency conversion technology is compressor noise and reliability, so the operating ratio above 120Hz More difficult.
  • the control method of the present invention is added, and when the rotation speed is fixed at 120 Hz, the refrigeration capacity can be increased to greatly expand the control range of the refrigeration capacity.
  • the control methods, b and c are used, it is possible to control the compressor refrigeration capacity in a state where the motor efficiency is the maximum speed to further improve the compressor efficiency.
  • For large load changes such as sudden liquid return in the compressor, quickly switching to mode 2 can prevent damage to the compressor. That is, it is advantageous for reliability.
  • the simple frequency conversion technique cannot quickly reduce the freezing capacity, nor can it avoid the sudden change of load.
  • control method provided by the present invention is a new capability control method applied to a product such as a 2-cylinder rotary compressor with a capacity control function, and provides seven different control methods.
  • a product such as a 2-cylinder rotary compressor with a capacity control function
  • seven different control methods for low-capacity control, one of the cylinders can be fixed to mode two, and the other cylinder can be independently switched between mode one and mode two.
  • the control method for stopping and starting the compressor proposed by the present invention is not only capable of controlling vibration and noise, but also superior in terms of energy saving and reliability. Further, by adding the function of the high and low pressure difference maintaining means, the compressor freezing capacity control method of the present invention can be more easily applied.
  • the invention is described by taking a two-cylinder rotary compressor with cylinder displacements of 65% and 35% respectively, but the control method proposed by the invention can be used for multi-gas simple rotary compression of more than two cylinders.
  • the cylinder displacement can also be changed, such as 80% and 20%, 70% and 30% or 60% and 40%, etc., according to specific needs Choose the right number of cylinders and cylinder displacement.
  • control technology and the frequency conversion technology can be combined to exert a mutually beneficial effect.

Landscapes

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

Abstract

A controlling method of a rotary compressor. Two or more cylinders (12,13) with different volumes are disposed in the compressor (1). In each cylinder (12,13) are respectively provided a piston (14.1,14.2), an eccentric crankshaft (17) for driving the piston (14.1,14.2) to rotate, and bearings (18.1,18.2) for supporting the eccentric crankshaft (17). A spring-loaded sliding vane (16.2) is disposed within a sliding vane slot (15.2) of at least one cylinder (13). The cylinders (12,13) carry out capacity switching in the way of compression and non-compression, wherein the cylinder compressing operation is referred as Mode One and the cylinder non-compressing operation is referred as Mode Two. A valve device (8) is provided outside of the compressor (1), which switches the sliding vane chamber pressure of the cylinders (12,13) between a high pressure and a low pressure via a high pressure and a low pressure which are brought by the compressor (1) during its operation. During its whole operation, the compressor (1) adopts one or more of seven operation ways to operate, singly or in combination, thereby controlling the capacity and freezing ability of the compressor.

Description

旋转压缩机的控制方法 技术领域  Control method for rotary compressor
本发明涉及一种旋转压缩机的控制方法， 特别是一种二汽缸旋转压缩 机冷冻能力的控制方法。  The present invention relates to a control method for a rotary compressor, and more particularly to a method for controlling the refrigeration capacity of a two-cylinder rotary compressor.
背景技术  Background technique
现在， 利用变频技术控制带变频功能的旋转式压缩机以控制其冷冻倉 I 力变化的手段已非常成熟，且已实现商品化，其主要是通过控制旋转式压缩 机的转速在约 15Hz (相当于排量的 25% )到约 120Hz (相当于排量的 200% ) 之间变化来实现。 （注： 相当于排量的 25%或者 200%, 即可认为变频技术 在压缩机排量 25%到 200%之间的范围内是连续可变的。 )但是， 最近从提 高舒适度和节能的观点来看，进一步降低转速和减少最小能力的需求逐渐增 加，由于润滑泵体的性能低下和润滑油膜的形成不充分会造成可靠性和振动 大幅增加的问题， 所以进一步降低转速是一个大的课题。  Nowadays, the use of variable frequency technology to control rotary compressors with variable frequency function to control the change of the pressure of the freezer compartment is very mature and has been commercialized, mainly by controlling the rotational speed of the rotary compressor at about 15 Hz (equivalent This is achieved by a change between 25% of the displacement and about 120 Hz (equivalent to 200% of the displacement). (Note: Equivalent to 25% or 200% of the displacement, it can be considered that the frequency conversion technology is continuously variable within the range of 25% to 200% of the compressor displacement.) However, recently improved comfort and energy saving From the point of view, the demand for further reduction of the rotational speed and the reduction of the minimum capacity is gradually increasing, and the lowering of the rotational speed is a large problem due to the low performance of the lubricating pump body and the insufficient formation of the lubricating oil film, which causes a problem of a large increase in reliability and vibration. Question.
针对这一点， 当压缩机转速一定， 及定速二汽缸旋转式压缩机在改变 冷冻能力的容量控制研究方面较有进展，并即将实现商品化。这种容量控制 就是使滑片在汽缸滑片槽内固定或解除固定，来改变汽缸排量的总量从而控 制冷冻能力的容量控制技术。变频技术是通过改变压缩机的转速来控制冷冻 能力， 故其控制方法比较单纯。 与其相比较， 容量控制技术可以在一个或二 个汽缸中通过压缩和非压缩作用的组合来改变冷冻能力，其控制技术和计算 方式是非常重要的。 在这里提供的技术是容量控制式二汽缸旋转式压缩机， 不光与冷冻能力控制方法相关，与作为课题的最小冷冻能力无限减小控制技 术也有关。 因此， 需要二个汽缸进行独立压缩和非压缩的容量控制。 由于这 样的容量控制旋转式压缩机的转速是一定的，因此不需要担心最小冷冻能力 时的润滑问题和振动问题。对于最小的制冷能力而言，上述变频技术的例子 中，压缩机排量小于 25%以下是不能进行冷冻能力控制，比如***侧的要求： 当冷冻能力为 20%时需要压缩机停机。  In response to this, when the compressor speed is constant, and the fixed-speed two-cylinder rotary compressor has made progress in the research of capacity control for changing the refrigeration capacity, it is about to be commercialized. This capacity control is a capacity control technique that controls the freezing capacity by fixing or unshelving the slide in the cylinder slide groove to change the total amount of cylinder displacement. The frequency conversion technology controls the freezing capacity by changing the speed of the compressor, so the control method is relatively simple. In contrast, capacity control technology can change the refrigeration capacity in a combination of compression and non-compression in one or two cylinders, and its control techniques and calculations are very important. The technology provided here is a capacity-controlled two-cylinder rotary compressor, not only related to the refrigeration capacity control method, but also related to the minimum refrigeration capacity reduction control technology as a subject. Therefore, two cylinders are required for independent compression and non-compressed capacity control. Since the rotation speed of such a capacity-controlled rotary compressor is constant, there is no need to worry about lubrication problems and vibration problems at the time of minimum refrigeration capacity. For the case of the minimum cooling capacity, in the case of the above-mentioned inverter technology, if the displacement of the compressor is less than 25%, the refrigeration capacity control cannot be performed, for example, the system side requirement: When the refrigeration capacity is 20%, the compressor shutdown is required.
确认本 另一方面， 由于目前的容量控制技术不能象变频技术那样改变电机输 出功率，所以二个汽缸中有一个汽缸的排量要减小， 而另一个汽缸的排量增 大，也就是说二个汽缸的容积比率增加， 此时就存在电机效率和压缩机效率 降低的课题。 例如， 当二汽缸旋转式压缩机中小的一方的汽缸排量为 35% , 当排量为 35%的汽缸单独运行时， 可能要求冷冻能力只有 25%时， 故也需 要停机， 也就是说和变频技术存在同样的课题。 Confirmation On the other hand, since the current capacity control technology cannot change the motor output power like the frequency conversion technology, the displacement of one of the two cylinders is reduced, and the displacement of the other cylinder is increased, that is, two As the volume ratio of the cylinder increases, there is a problem that the motor efficiency and the compressor efficiency are lowered. For example, when the smaller one of the two-cylinder rotary compressor has a cylinder displacement of 35%, when the cylinder with a displacement of 35% is operated alone, it may require only 25% of the refrigeration capacity, so it is also required to stop, that is, Frequency conversion technology has the same problem.
上述二种冷冻能力控制技术中， 压缩机一旦停机， 由于压缩机电机启 动力矩的需要，直到***压力平衡后才可以再启动， 而通常情况下再启动需 要等待 3分钟以上。 因此， 按***要求的冷冻能力控制压缩机对外输出的冷 冻能力时， 需要反复停机和进行压缩机最小能力运行。 但是， 如果压缩机等 待再启动的时间过长， 而且失去高低压力差的***要上升到所需压力、恢复 原有功能， 则要浪费大量的时间和能源。 即是说， 用停机来控制冷冻能力的 控制方法从理论上来讲是很难顺利进行的， 即便是能进行， 其效率也存在极 大的问题。  In the above two kinds of refrigeration capacity control technologies, once the compressor is stopped, it can be restarted until the system pressure is balanced due to the need of the compressor motor starting torque. Normally, it takes more than 3 minutes to restart. Therefore, when controlling the refrigeration capacity of the compressor for external output according to the refrigeration capacity required by the system, it is necessary to repeatedly stop the machine and perform the minimum capacity operation of the compressor. However, if the compressor waits for a long time to restart, and the system that loses the high and low pressure difference rises to the required pressure and restores the original function, it will waste a lot of time and energy. That is to say, the control method of controlling the freezing capacity by stopping is theoretically difficult to carry out smoothly, and even if it can be carried out, the efficiency is extremely problematic.
发明内容  Summary of the invention
本发明所要解决的技术问题在于提供一种在容量控制旋转式压缩机的 基础上，进一步减小最小冷冻能力的低能力旋转压缩机的控制方法，使压缩 机内的两个及以上的汽缸压缩独立压缩或不压缩，以克服现有技术中的不足 之处。  The technical problem to be solved by the present invention is to provide a control method for a low-capacity rotary compressor that further reduces the minimum refrigeration capacity based on the capacity-controlled rotary compressor, and compresses two or more cylinders in the compressor. Independently compressed or uncompressed to overcome the deficiencies in the prior art.
本发明解决上述技术问题釆用的技术方案是： 一种旋转压缩机的控制 方法，压缩机内设置有两个及以上不同容积的汽缸，每个汽缸内分别设置有 活塞、驱动活塞运转的偏心曲轴及支撑偏心曲轴的轴承， 至少有一个汽缸的 滑片槽内设置有滑片弹簧， 汽缸以 :压缩和非压缩方式进行容量切换，将汽缸 压缩运行记为模式一，汽缸非压缩运行记为模式二，压缩机外设置有阀装置， 阀装置利用压缩机开始运行时产生的高压和低压使汽缸的滑片室压力在低 压和高压之间进行切换，压缩机在整个运行时间内采用下列七种运行方法中 的一种及以上的方法单独或组合运行， 其中， 以高容积汽缸为第一汽缸， 以 低容积汽缸为第二汽缸， 则有： The technical solution for solving the above technical problem is: a control method of a rotary compressor, wherein two or more cylinders of different volumes are disposed in the compressor, and each cylinder is provided with a piston and an eccentricity for driving the piston a crankshaft and the eccentric crankshaft bearing support, is provided with a slide groove has a slide spring of the cylinder at least to the cylinder: compressed and uncompressed size switching manner, the compression cylinder operating mode referred to as a cylinder running denoted uncompressed In mode 2, a valve device is disposed outside the compressor, and the valve device uses the high pressure and low pressure generated when the compressor starts to operate to switch the cylinder chamber pressure between the low pressure and the high pressure, and the compressor adopts the following seven times during the entire running time. One or more of the operating methods are operated separately or in combination, wherein the high volume cylinder is the first cylinder, The low volume cylinder is the second cylinder, then:
a ) 第一汽缸固定为模式一， 第二汽缸在模式一和模式二之间来回切换； b ) 第一汽缸在模式一和模式二之间来回切换， 第二汽缸固定为模式一； c ) 第一汽缸和第二汽缸分别在模式一和模式二之间相互切换；  a) the first cylinder is fixed to mode one, the second cylinder is switched back and forth between mode one and mode two; b) the first cylinder is switched back and forth between mode one and mode two, and the second cylinder is fixed to mode one; c) The first cylinder and the second cylinder are switched between mode one and mode two, respectively;
d ) 第一汽缸在模式一和模式二之间来回切换， 第二汽缸固定为模式二； e ) 第一汽缸固定为模式二， 第二汽缸在模式一和模式二之间来回切换； f ) 第一汽缸以模式一运行和模式三的切换， 第二汽缸固定为模式二； g ) 第一汽缸固定为模式二， 第二汽缸以模式一运行和模式三的切换； 其中， 压缩机停机， 釆用模式一将运行中的汽缸切换到模式二后停机, 此时电源关闭， 接着压缩机启动， 将汽缸保持在模式二的状态启动， 此时电 源打开，然后压缩机运行加速稳定后，再切换到模式一运行的过程为模式三。  d) the first cylinder switches back and forth between mode one and mode two, the second cylinder is fixed to mode two; e) the first cylinder is fixed to mode two, and the second cylinder is switched back and forth between mode one and mode two; f) The first cylinder is switched between mode one mode and mode three, the second cylinder is fixed to mode two; g) the first cylinder is fixed to mode two, and the second cylinder is switched by mode one mode and mode three; wherein, the compressor is stopped, In the first mode, the running cylinder is switched to the mode 2 and then stopped. At this time, the power is turned off, then the compressor is started, and the cylinder is kept in the mode 2 state. At this time, the power is turned on, and then the compressor is running stably, then The process of switching to mode one is mode three.
本发明提供的控制方法可以固定在电机效率为最大转速的状态下控制 压缩机冷冻能力， 以更进一步地改善压缩机效率，且在控制过程中压缩机本 身不停机， 既不消耗压缩机启动和启动后所需的多余电力， 又可防止效率低 下， 并可预防启动或停止时产生的振动， 还可防止启动时产生的负荷， 如液 态冷媒吸入或油面低下等， 且不影响压缩机的可靠性。  The control method provided by the invention can fix the compressor refrigeration capacity under the condition that the motor efficiency is the maximum speed to further improve the compressor efficiency, and the compressor itself does not stop during the control process, and does not consume the compressor start and Excessive power required after start-up prevents inefficiency and prevents vibrations generated during start or stop. It also prevents loads generated during start-up, such as liquid refrigerant suction or oil level, without affecting the compressor. reliability.
采用本控制方法的压缩机在一定的时间 Tc中， 如果适当延长模式二的 总运行时间， 压缩机对外提供的冷冻能力可以接近 0%， 而这些优点是以前 的变频压缩机和以前的二汽缸式容量控制方法中所不具有的。 The compressor using the control method can increase the total running time of mode 2 by a certain period of time T c , and the refrigeration capacity provided by the compressor can be close to 0%, and these advantages are the former inverter compressor and the former two. Not available in the cylinder type capacity control method.
附图说明  DRAWINGS
图 1为本发明一实施例结构示意图。 ，  1 is a schematic structural view of an embodiment of the present invention. ,
图 2为二汽缸的旋转压缩机剖视结构示意图。  2 is a cross-sectional structural view of a two-cylinder rotary compressor.
图 3为二汽缸的冷冻能力计算表。  Figure 3 shows the calculation of the refrigeration capacity of the two cylinders.
具体实施方式  detailed description
下面结合附图及实施例对本发明作进一步描述。  The invention is further described below in conjunction with the drawings and embodiments.
下面结合附图及实施例对本发明作进一步描述。 图中， 1为压缩机， 2为储液器， 3为排气管， 4为冷凝器， 5为自动膨 胀阀， 6为蒸发器， 7为单向阀， 8为阀装置， 10为压缩组件， 11为电机组 件， 12为第一汽缸， 13为第二汽缸， 14.1为第一活塞， 14.2为第二活塞， 15.1为第一滑片槽， 15.2为第二滑片槽， 16.1为第一滑片， 16.2为第二滑片， 17为偏心曲轴主轴， 18.1为上轴承， 18,2为下轴承， 19为偏心曲轴副轴， 20.1为第一滑片室， 20.2为第二滑片室， 21为第一压力切换管， 22为第二 压力切换管， 23为低压管， 24为高压管， 33为中间隔板。 The invention is further described below in conjunction with the drawings and embodiments. In the figure, 1 is the compressor, 2 is the accumulator, 3 is the exhaust pipe, 4 is the condenser, 5 is the automatic expansion valve, 6 is the evaporator, 7 is the check valve, 8 is the valve device, 10 is the compression The assembly, 11 is the motor assembly, 12 is the first cylinder, 13 is the second cylinder, 14.1 is the first piston, 14.2 is the second piston, 15.1 is the first sliding vane, 15.2 is the second sliding vane, 16.1 is the first a sliding piece, 16.2 is the second sliding piece, 17 is the eccentric crankshaft main shaft, 18.1 is the upper bearing, 18, 2 is the lower bearing, 19 is the eccentric crankshaft countershaft, 20.1 is the first sliding vane chamber, and 20.2 is the second sliding vane Room, 21 is the first pressure switching tube, 22 is the second pressure switching tube, 23 is the low pressure tube, 24 is the high pressure tube, and 33 is the intermediate partition.
参见图 1 , 为使用了本控制方法的旋转式压缩机冷冻循环结构示意图， 旋转式压缩机 1压缩从储液器 2吸入的低压气体,压缩后通过排气管 3排出 高压气体。 之后， 在冷凝器 4冷凝的液体冷媒通过自动膨胀阀 5减压， 在蒸 发器 6蒸发， 低压冷媒回到储液器 2中， 再次被吸入压缩机 1中压缩。 蒸发 器 6和储液器 2之间安装的单向阀 7将作为后述高低差压维持装置使用。  Referring to Fig. 1, a schematic diagram of a refrigerating cycle of a rotary compressor using the present control method, the rotary compressor 1 compresses the low-pressure gas sucked from the accumulator 2, and compresses and discharges the high-pressure gas through the exhaust pipe 3. Thereafter, the liquid refrigerant condensed in the condenser 4 is depressurized by the automatic expansion valve 5, evaporated in the evaporator 6, and the low-pressure refrigerant is returned to the accumulator 2, and is again sucked into the compressor 1 for compression. The check valve 7 installed between the evaporator 6 and the accumulator 2 will be used as a high and low differential pressure maintaining device to be described later.
阀装置 8设置在压缩机 1的外部， 阀装置可于压缩机的运行中控制二 气缸独立进行汽缸压缩或者停止 , 以实现压缩机冷冻能力分阶段切换， 故此 二个汽缸排量的设计有所不同。  The valve device 8 is disposed outside the compressor 1. The valve device can control the two cylinders to independently perform cylinder compression or stop during the operation of the compressor, so as to realize the phased switching of the compressor refrigeration capacity, so the design of the two cylinder displacements is different.
以空调的制冷运行为例说明： 在盛夏酷署， 当刚开始进行制冷时， 因 其迅速， 故需要压缩机提供最高的制冷能力， 当室温降至目标温度附近时， 压缩机运行切换到中间能力以减少制冷能力， 当室温进一步接近目标温度 时， 压缩机再次切换到低的制冷能力。 因此， 根据需要制冷的房间热负荷及 时切换制冷能力， 可在营造舒适空气调节的同时， 防止能量浪费， 以提高空 调效率。带容量控制旋转式压缩机与变频式的旋转式压缩机能力控制作用相 同， 或者是更进一步的能力控制。  Take the cooling operation of the air conditioner as an example: In the midsummer cool department, when it starts to cool, because it is fast, the compressor needs to provide the highest cooling capacity. When the room temperature drops to the target temperature, the compressor runs to the middle. The ability to reduce the cooling capacity, when the room temperature is further close to the target temperature, the compressor switches to low cooling capacity again. Therefore, depending on the heat load of the room to be cooled and the ability to switch the cooling capacity, it is possible to prevent the waste of energy while creating a comfortable air conditioning to improve the air conditioning efficiency. The rotary compressor with capacity control has the same function as the variable-capacity rotary compressor, or it has further capability control.
参见图 2, 为二汽缸的旋转式压缩机内部构造结构示意图。旋转式压缩 机 1的密封壳体内部安装了压缩组件 10和电机组件 11。 压缩组件 10包括 第一汽缸 12和第二汽缸 13; 第一汽缸 12内设置有第一活塞 14.1 , 第一汽 缸 12的第一滑片槽 15.1中安装有第一滑片 16.1 , 第二汽缸 13内设置有第 二活塞 14,2， 第二汽缸 13的第二滑片槽 15.2中安装有第二滑片 16.2; 同时 驱动第一活塞 14.1和第二活塞 14.2的偏心曲轴 17 , 支撑偏心曲轴 17的上 轴承 18.1和下轴承 18.2。 其中， 偏心曲轴 17通过电机组件 11驱动， 以一 定速度（60或 50Hz )运行， 并将力矩传递给活塞。 第一汽缸 12的第一滑 片室 20.1与第一压力切换管 21相接， 第二汽缸 13的第二滑片室 20.2与第 二压力切换管 22相接， 各切换管的一端均与阀装置 8相接。 连接阀装置 8 的低压管 23的一端与压缩机 1的吸入管等低压部分相接， 连接阀装置 8壳 体内部的高压管 24与压缩机 1的壳体内部相接。 阀装置 8利用压缩机开始 运行时产生的高压和低压，使第一汽缸 12和笫二汽缸 13的滑片室压力在低 压和高压之间进行切换。 因此， 二个汽缸都可以收纳固定滑片以停止压缩， 即模式二， 以及解除滑片固定以开始压缩， 即模式一。 并且， 阀装置 8具有 使每个汽缸模式独立并相互切换的功能。 Referring to Fig. 2, it is a schematic structural view of the internal structure of a two-cylinder rotary compressor. A compression assembly 10 and a motor assembly 11 are mounted inside the sealed casing of the rotary compressor 1. The compression assembly 10 includes a first cylinder 12 and a second cylinder 13; a first piston 14.1 is disposed in the first cylinder 12, and a first slide 16.1 is mounted in the first vane slot 15.1 of the first cylinder 12, and the second cylinder 13 is mounted. a second piston 14, 2 is disposed therein, and a second sliding plate 16.2 is mounted in the second sliding groove 15.2 of the second cylinder 13; An eccentric crankshaft 17 that drives the first piston 14.1 and the second piston 14.2 supports the upper bearing 18.1 and the lower bearing 18.2 of the eccentric crankshaft 17. Among them, the eccentric crankshaft 17 is driven by the motor assembly 11, operates at a certain speed (60 or 50 Hz), and transmits torque to the piston. The first sliding chamber 20.1 of the first cylinder 12 is in contact with the first pressure switching tube 21, and the second sliding chamber 20.2 of the second cylinder 13 is connected to the second pressure switching tube 22, and one end of each switching tube is connected to the valve. The device 8 is connected. One end of the low pressure pipe 23 of the connection valve device 8 is in contact with a low pressure portion such as a suction pipe of the compressor 1, and the high pressure pipe 24 inside the casing of the connection valve device 8 is in contact with the inside of the casing of the compressor 1. The valve unit 8 uses the high pressure and low pressure generated when the compressor starts operating, so that the vane chamber pressures of the first cylinder 12 and the second cylinder 13 are switched between low pressure and high pressure. Therefore, both cylinders can accommodate the fixed slide to stop the compression, that is, mode two, and release the slide to start the compression, that is, mode one. Further, the valve device 8 has a function of making each cylinder mode independent and switching to each other.
参见图 3 , 图中按压缩机的冷冻能力分为三个范围， 分别为 100~65% 的高域范围、 65~35%的中域范围和 35~0%的低域范围。 以二汽缸的旋转式 压缩机的排量总量为 100% (比如 40cc ), 各自的排量分别为： 第一汽缸占 65% (即 26cc )和第二汽缸占 35% (即 14cc ), 对压缩机冷冻能力的控制计 算方法进行具体说明。 其中， 一定时问范围内， 压缩机对外提供的冷冻能力 为二个汽缸分别提供的冷冻能力的总和。  Referring to Figure 3, the compressor is divided into three ranges according to the refrigeration capacity of the compressor, which are 100~65% high range, 65~35% medium range and 35~0% low range. The displacement of the two-cylinder rotary compressor is 100% (such as 40cc), and the respective displacements are: the first cylinder accounts for 65% (ie 26cc) and the second cylinder accounts for 35% (ie 14cc). The control calculation method of the compressor refrigeration capacity will be specifically described. Among them, within a certain time range, the refrigeration capacity provided by the compressor is the sum of the refrigeration capacity provided by the two cylinders respectively.
首先是控制方法 ， 在一定时间 TC内， 第一汽缸固定为模式一运行， 第二汽缸在模式一和模式二之间来回切换。将第一汽缸或者第二汽缸中模式 一的总运行时间分别记为 TAI和 TB1， TA1/TC或者 TB1/TC即为各自的运行时 间比率。 比如， 10分钟内， 即 TC=10, 模式一运行进行 3次， 其总时间为 6 分钟， 则有 TA1/Tc：、 或者 TB1/TC为 6/10=0.6。 则有总的冷冻能力为 65+35XTBI/TC =:65+35X0.6=86O 因此， 10分钟内， 即 TC=10时， 压缩机对外 提供的冷冻能力为其总冷冻冷力的 86%。 The first is the control method. During a certain time T C , the first cylinder is fixed to mode one operation, and the second cylinder is switched back and forth between mode one and mode two. The total running time of mode one in the first cylinder or the second cylinder is respectively recorded as TAI and T B1 , and T A1 /T C or T B1 /T C is the respective running time ratio. For example, within 10 minutes, that is, T C = 10, mode 1 is run 3 times, and the total time is 6 minutes, then T A1 /Tc:, or T B1 /T C is 6/10=0.6. The total refrigeration capacity is 65+35XTBI/T C =: 65+35X0.6=86 O. Therefore, within 10 minutes, ie T C =10, the external refrigeration capacity of the compressor is its total refrigeration capacity. 86%.
另一方面， 如果在 TC时间内， 第一汽缸或第二汽缸的模式二的总运行 时间分别为 TA。或者 TB。， 则 TAQ/TC或者 TB。/TC就是在每个汽缸以模式二的 运行时间比率。 由于 TA1+ TA0=TC, 或者 TB1+ TBO =Tc, 所以假如在不知道 TA1和 1^情况下， 如果知道 TAo或者 TB0, 那么也可以求到冷冻能力。 On the other hand, if the time is T C , the total operating time of mode two of the first cylinder or the second cylinder is T A , respectively. Or T B . , then T AQ /T C or T B . /T C is the ratio of run time in mode 2 for each cylinder. Since T A1 + T A0 = T C , or T B1 + TBO = T c , if you don't know In the case of T A1 and 1^, if T A o or T B0 is known , the freezing ability can also be obtained.
控制方法 b与控制方法 a基本相同， 其区别仅仅在于第一汽缸在模式 一和模式二之间来回切换，而第二汽缸固定为模式一运行， 故其计算过程同 控制方法 ， 不再重复。 压缩机对外提供的冷冻能力为 35+65xTA1/Tc。 The control method b is basically the same as the control method a, except that the first cylinder is switched back and forth between mode one and mode two, and the second cylinder is fixed to mode one operation, so the calculation process is the same as the control method and is not repeated. The external refrigeration capacity of the compressor is 35+65xT A1 /T c .
控制方法 c为将第一汽缸和第二汽缸的运行模式在模式一和模式二之 间相互切换进行能力控制， 也就是说， 在同一时间内， 第一气缸和第二气缸 中仅有一个汽缸进行压缩， 处于模式一， 而另一个则非压缩， 处于模式二， 并有 TA1+TB1=TC。 压缩机对外提供的冷冻能力为 65xTA1/Tc+35xTB1/Tc。 The control method c is to control the operation modes of the first cylinder and the second cylinder to switch between mode 1 and mode 2, that is, at the same time, only one of the first cylinder and the second cylinder Compression is in mode one, while the other is uncompressed, in mode two, and there is T A1 +T B1 =T C . The compressor provides a refrigeration capacity of 65xT A1 /T c +35xT B1 /T c .
接下来是控制方法 d， 第一汽缸在模式一和模式二之间来回切换， 第二 汽缸固定为模式二， 则有第二汽缸的冷冻能力为 0, 因此， 压缩机对外提供 的冷冻能力为 65 x TA1/Tc。在这种控制方法 d中， 第一汽缸间断地重复压缩 和非压缩运行。 Next is the control method d, the first cylinder is switched back and forth between mode one and mode two, the second cylinder is fixed to mode two, and the second cylinder has a freezing capacity of 0. Therefore, the externally provided refrigeration capacity of the compressor is 65 x T A1 /T c . In this control method d, the first cylinder intermittently repeats the compression and non-compression operations.
在这里值得注意的是， 由于第一汽缸是采用模式一和模式二切换， 如 果减小 65xTA1/Tc到一定程度， 那么压缩机对外提供的冷冻能力完全可以控 制到 35%以下。 ' It is worth noting here that since the first cylinder is switched between mode one and mode two, if the 65xT A1/ T c is reduced to a certain extent, the refrigeration capacity provided by the compressor can be controlled to less than 35%. '
控制方法 e与控制方法 d则相反，控制方法 e以第一汽缸固定为模式二, 第二汽缸在模式一和模式二之间来回切换， 则有第一汽缸的冷冻能力为 0, 因此， 压缩机对外提供的冷冻能力为 35xTBl/TC。 在这种控制方法 e中， 第 二汽缸间断地重复压缩和非压缩运行。  The control method e is opposite to the control method d. The control method e is fixed to the mode 2 by the first cylinder, and the second cylinder is switched back and forth between the mode 1 and the mode 2, and the freezing capacity of the first cylinder is 0, therefore, the compression The external refrigeration capacity provided by the machine is 35xTBl/TC. In this control method e, the second cylinder intermittently repeats the compression and non-compression operations.
下面将具体介绍控制方法 d和控制方法 e的优点。  The advantages of the control method d and the control method e will be specifically described below.
1 )压缩机对外提供的冷冻能力可降低为 35%以下，  1) The refrigeration capacity provided by the compressor can be reduced to less than 35%.
特别是在一定的时间 Tc中， 适当延长模式二的总运行时间， 从理论上 来说， 压缩机对外提供的冷冻能力可以接近 0%， 而这些优点是以前的变频 压缩机和以前的二汽缸式容量控制方法中所不具有的。 Especially in a certain time T c , the total running time of mode 2 is appropriately extended. Theoretically, the externally provided refrigeration capacity of the compressor can be close to 0%, and these advantages are the previous inverter compressor and the previous two cylinders. Not available in the volume control method.
2 )压缩机不停机，  2) The compressor does not stop,
因此， 汽缸的模式切换就显得相当容易， 也不消耗压缩机启动和启动 后所需的多余电力、又可防止效率低下，并可预防启动或停止时产生的振动， 还可防止启动时产生的负荷 （如液态冷媒吸入或油面低下等）， 且不影响压 缩机的可靠性。 Therefore, the mode switching of the cylinder is quite easy, does not consume the excess power required after the compressor is started and started, prevents inefficiency, and prevents vibration generated during starting or stopping. It also prevents the load generated during start-up (such as liquid refrigerant suction or low oil level) without affecting the reliability of the compressor.
最后是控制方法 f和控制方法 g, 这 2种方法中的第一汽缸（65% )或 者第二汽缸（35% )中的任何一方固定为模式二， 即非压缩运行， 另一方以 模式一运行和模式三切换。 其中，压缩机停机， 釆用模式一将运行中的汽缸 切换到模式二后停机， 此时电源关闭， 接着压缩机启动， 将汽缸保持在模式 二的状态启动， 此时电源打开， 然后， 压缩机运行加速稳定后（通常 1秒左 右）， 再切换到模式一运行的过程为模式三。  Finally, the control method f and the control method g, either of the first cylinder (65%) or the second cylinder (35%) of the two methods are fixed to mode two, that is, non-compression operation, and the other mode is mode one. Run and mode three switch. Among them, the compressor is stopped, the first mode is to switch the running cylinder to the second mode, then the power is turned off, then the compressor starts, the cylinder is kept in the mode 2 state, then the power is turned on, then, the compression After the machine runs at an accelerated speed (usually about 1 second), the process of switching to mode one is mode three.
釆用模式三停止和启动具有如下优点：  The use of mode three stop and start has the following advantages:
1 )停机前压缩机处于压缩停止的无负荷状态；  1) The compressor is in a no-load state with compression stop before stopping;
2 )启动后也是无负荷状态， 此时处于模式二， 故不产生压缩力矩。  2) After starting, it is also in a no-load state. At this time, it is in mode 2, so no compression torque is generated.
3 )启动和停机时无震动， 启动容易， 启动力矩可减小；  3) No vibration when starting and stopping, easy to start, and the starting torque can be reduced;
4 ) 防止启动时浪费多余电力。  4) Prevent unnecessary power from being wasted at startup.
将控制方法 f和 g进行比较，控制方法 g可以使用较小排量的第二汽缸 ( 35% ), 所以和控制方法 f 相比可以较精确和容易地控制压缩机对外提供 的冷冻能力。 也就是说 35%以下的能力控制中使用排量比较小的第二汽缸, 在冷冻能力控制的微调和压缩机启动方面比较有优势。  Comparing the control methods f and g, the control method g can use the second cylinder (35%) with a smaller displacement, so that the externally provided refrigeration capacity can be controlled more accurately and easily than the control method f. That is to say, the second cylinder with a relatively small displacement is used in the capacity control of less than 35%, which is advantageous in the fine adjustment of the refrigeration capacity control and the startup of the compressor.
因此， 第二汽缸排量 35%以下的低域进行能力控制时， 推荐将排量大 的一方的第一汽缸作为模式二，小的第二汽缸作为模式一和模式二或者模式 三进行能力控制。  Therefore, when the second cylinder displacement is less than 35% of the low-range capacity control, it is recommended to use the first cylinder with the larger displacement as the mode 2 and the smaller second cylinder as the mode 1 and mode 2 or mode 3 for the capacity control. .
如果采用控制方法 f和 g对压缩机停机和启动来控制能力时，排量小的 第二汽缸要事先切换为模式二。第二汽缸的控制过程是模式一→模式二 模 式三→模式二启动 模式一。  If the control methods f and g are used to control the compressor shutdown and start, the second cylinder with a small displacement must be switched to mode two beforehand. The control process of the second cylinder is mode one → mode two mode three → mode two start mode one.
至于 2个汽缸内至少有 1个汽缸需要装滑片弹簧， 最好在排量小的第 二汽缸中装设，其原因在于如果压缩机停机时间过长，***内的高低压会趋 于平衡， 而压缩机压缩运行时， 即模式一运行， 需要滑片弹簧。  As for at least one cylinder in two cylinders, it is necessary to install a vane spring, preferably in a second cylinder with a small displacement. The reason is that if the compressor is down for too long, the high and low pressures in the system will tend to balance. When the compressor is running in compression, that is, mode one operation, a slide spring is required.
对于时间 Tc的设定， 及模式一运行和模式二运行时间的设定， 切换 的次数和压缩机冷冻能力的变动幅度有关， 都需要通过具体***进行优化。 本发明还可以在一定的时间范围内通过将不同的控制方法组合起来 使用， 可取得不同的压缩机冷冻能力， 至于具体的模式一和模式二的运行时 间设定同样需要根据具体***予以设计。 For the setting of time T c , and the setting of mode one operation and mode two running time, switching The number of times is related to the variation of the compressor's refrigeration capacity, and needs to be optimized through a specific system. The present invention can also achieve different compressor refrigeration capacities by combining different control methods within a certain time range. As for the specific mode 1 and mode 2 run time settings, it is also necessary to design according to the specific system.
特别值得注意的是釆用控制方法 d、 e f 和 g时， 如果模式二运行 或者压缩机停止时间长， ***或者压缩机的高低压力差将减小，致使不能进 行模式切换或模式保持。但是，对于这个课题如果使用如图 1那样的高低压 力差维持装置就可以得到大幅度改善，见图 1 , 于冷凝器 4和蒸发器 6之间 设置自动膨胀阀 5; 另外， 压缩机吸入回路和蒸发器 6之间设置单向阀 7。 那么，在控制方法 e或者 g中， 第二汽缸在模式二运行中或者是在压缩机停 机时， 自动膨胀阀 5全闭， 可以有效防止从冷凝器（高压侧）到蒸发器（低 压侧）的气体流失。 而且， 从压缩机壳体（高压側）到蒸发器（低压側）泄 漏的气体也可以通过单向阀 7予以阻止。 即，模式二的运行时间或压缩机停 止时间得到可以延长， 控制也相对容易。  It is particularly noteworthy that when the control methods d, e f and g are used, if mode 2 is operated or the compressor is stopped for a long time, the high or low pressure difference of the system or compressor will be reduced, resulting in mode switching or mode keeping. However, if this problem is to be improved by using a high and low pressure difference maintaining device as shown in Fig. 1, as shown in Fig. 1, an automatic expansion valve 5 is provided between the condenser 4 and the evaporator 6. In addition, the compressor suction circuit A check valve 7 is provided between the evaporator 6. Then, in the control method e or g, when the second cylinder is in mode two operation or when the compressor is stopped, the automatic expansion valve 5 is fully closed, which can effectively prevent the condenser (high pressure side) from the evaporator (low pressure side). Gas loss. Moreover, the gas leaking from the compressor casing (high pressure side) to the evaporator (low pressure side) can also be blocked by the check valve 7. That is, the operation time of the mode 2 or the compressor stop time can be extended, and the control is relatively easy.
如上所述， 通过使用压力差维持装置， 模式切换就变得很容易， 可以 解决上述课题。并且，压力差维持装置可以缩短压缩机开始压缩后***到达 设定条件所需的过渡时间， 所以可以缩短空调***过渡的时间以及改善效 率。 而且， 单向阀可以阻止压缩机压缩作用停止后， 产生的从压缩机壳体到 蒸发器的高压气体的逆流。为了实现压力差维持而釆用的压力差维持装置应 该有许多不同的方法和不同的结构 ,这里仅仅以自动膨胀阀和单向阀为代表 进行说明，比如简单的应用单向阀的动作使冷凝器和蒸发器之间的回路自动 关闭。在使用变频技术改变压缩机回转速度的旋转式压缩机中釆用本发明中 的控制方法，可极大的改善压缩机工作效率和扩大压缩机的冷冻能力控制范 围。 例如， 压缩机转速固定为 15Hz时， 如果釆用控制方法 d或者 e， 压缩 机的对外提供的冷冻能力就可以更小，并可以改善压缩机效率和提高空调精 度。  As described above, by using the pressure difference maintaining means, mode switching becomes easy, and the above problem can be solved. Further, the pressure difference maintaining means can shorten the transition time required for the system to reach the set condition after the compressor starts to be compressed, so that the transition time of the air conditioning system can be shortened and the efficiency can be improved. Moreover, the check valve can prevent the reverse flow of the high pressure gas generated from the compressor casing to the evaporator after the compression of the compressor is stopped. In order to achieve the pressure difference maintenance, the pressure difference maintaining device should have many different methods and different structures. Here, only the automatic expansion valve and the check valve are represented, for example, the simple application of the check valve action causes condensation. The circuit between the evaporator and the evaporator is automatically turned off. In the rotary compressor using the variable frequency technique to change the rotational speed of the compressor, the control method of the present invention can greatly improve the working efficiency of the compressor and expand the control range of the refrigeration capacity of the compressor. For example, when the compressor speed is fixed at 15 Hz, if the control method d or e is used, the external cooling capacity of the compressor can be made smaller, and the compressor efficiency and air conditioning accuracy can be improved.
变频技术的课题是压缩机噪音和可靠性， 所以在 120Hz以上的运行比 较困难。 但是， 如果事先将压缩机排量设计得比较大， 追加本发明的控制方 法， 在转速固定为 120Hz 时可以增加冷冻能力， 以大幅度扩大冷冻能力的 控制范围。 当使用控制方法 、 b和 c时， 可以固定在电机效率为最大转速 的状态下控制压缩机冷冻能力， 以更进一步地改善压缩机效率。针对压缩机 中突然出现回液现象等大负荷变动，迅速切换为模式二可防止对压缩机的伤 害。 即， 对可靠性是有利的。 但是， 单纯的变频技术是不能够迅速降低冷冻 能力， 也不能回避突然变化的负荷。 The subject of frequency conversion technology is compressor noise and reliability, so the operating ratio above 120Hz More difficult. However, if the compressor displacement is designed to be relatively large in advance, the control method of the present invention is added, and when the rotation speed is fixed at 120 Hz, the refrigeration capacity can be increased to greatly expand the control range of the refrigeration capacity. When the control methods, b and c are used, it is possible to control the compressor refrigeration capacity in a state where the motor efficiency is the maximum speed to further improve the compressor efficiency. For large load changes such as sudden liquid return in the compressor, quickly switching to mode 2 can prevent damage to the compressor. That is, it is advantageous for reliability. However, the simple frequency conversion technique cannot quickly reduce the freezing capacity, nor can it avoid the sudden change of load.
综上所述， 本发明提供的控制方法是应用于带容量控制功能的 2汽缸 旋转式压缩机等产品中的新能力控制手段，可提供 7种不同控制方法。特别 是为进行低能力控制时， 可使其中一方的汽缸固定为模式二，另一个汽缸在 模式一和模式二之间独立进行模式切换。本发明提出的压缩机的停止和启动 的控制方法不光是可以控制振动和噪声，从节能和可靠性的观点来看也是优 越的。 并且， 通过追加高低压力差维持装置的功能， 将使本发明的压缩机冷 冻能力控制方法更为容易应用。  In summary, the control method provided by the present invention is a new capability control method applied to a product such as a 2-cylinder rotary compressor with a capacity control function, and provides seven different control methods. In particular, for low-capacity control, one of the cylinders can be fixed to mode two, and the other cylinder can be independently switched between mode one and mode two. The control method for stopping and starting the compressor proposed by the present invention is not only capable of controlling vibration and noise, but also superior in terms of energy saving and reliability. Further, by adding the function of the high and low pressure difference maintaining means, the compressor freezing capacity control method of the present invention can be more easily applied.
本发明是以二汽缸旋转式压缩机， 汽缸排量分别为 65%和 35%为例作 出说明的，但是，本发明提出的控制方法完全可以用在二汽缸以上的多气简 式旋转式压缩机中， 如 3汽缸、 4汽缸或 5汽缸等等， 而且， 汽缸排量也可 做变化， 如 80%和 20%、 70%和 30%或 60%和 40%等等， 可根据具体需要 选择合适的汽缸数目和汽缸排量。  The invention is described by taking a two-cylinder rotary compressor with cylinder displacements of 65% and 35% respectively, but the control method proposed by the invention can be used for multi-gas simple rotary compression of more than two cylinders. In the machine, such as 3 cylinders, 4 cylinders or 5 cylinders, etc., and the cylinder displacement can also be changed, such as 80% and 20%, 70% and 30% or 60% and 40%, etc., according to specific needs Choose the right number of cylinders and cylinder displacement.
在使用变频技术的旋转式压缩机中采用本发明的容量控制方法， 可将 本控制技术和变频技术结合起来发挥出相得益彰的效果。  By adopting the capacity control method of the present invention in a rotary compressor using a variable frequency technology, the control technology and the frequency conversion technology can be combined to exert a mutually beneficial effect.

Claims

杈 利 要 求 书 Profit request
1.一种旋转压缩机的控制方法， 压缩机内设置有两个及以上不同容积的汽 缸， 每个汽缸内分别设置有活塞、 驱动活塞运 的偏心曲轴及支撑偏心曲轴的 轴承， 至少有一个汽缸的滑片槽内设置有滑片弹簧， 汽缸以压缩和非压缩方式 进行容量切换， 将汽缸压缩运行记为模式一， 汽缸非压缩运行记为模式二， 压 缩机外设置有阀装置 （8 ) , 阀装置利用压缩机开始运行时产生的高压和低压 使汽缸的滑片室压力在低压和高压之间进行切换， 其特征是所述的压缩机在整 个运行时间内采用下列七种运行方法中的一种及以上的方法单独或组合运行， 其中， 以高容积汽缸为第一汽缸， 以低容积汽缸为第二汽缸， 则有： A control method for a rotary compressor, wherein two or more cylinders of different volumes are disposed in the compressor, and each cylinder is provided with a piston, an eccentric crankshaft for driving the piston, and a bearing for supporting the eccentric crankshaft, at least one A vane spring is arranged in the vane groove of the cylinder, the cylinder is switched in capacity in a compressed and uncompressed manner, the cylinder compression operation is recorded as mode one, the cylinder non-compressed operation is recorded as mode two, and the compressor is provided with a valve device (8) The valve device uses the high pressure and low pressure generated when the compressor starts to operate to switch the cylinder chamber pressure between the low pressure and the high pressure, which is characterized in that the compressor adopts the following seven operating methods throughout the running time. One or more of the above methods are operated alone or in combination, wherein the high volume cylinder is the first cylinder and the low volume cylinder is the second cylinder, then:
a ) 第一汽缸固定为模式一， 第二汽缸在模式一和模式二之间来回切换； b )第一汽缸在模式一和模式二之间来回切换， 笫二汽缸固定为模式一； c )第一汽缸和第二汽缸分别在模式一和模式二之间相互切换；  a) the first cylinder is fixed to mode one, the second cylinder is switched back and forth between mode one and mode two; b) the first cylinder is switched back and forth between mode one and mode two, and the second cylinder is fixed to mode one; c) The first cylinder and the second cylinder are switched between mode one and mode two, respectively;
d ) 第一汽缸在模式一和模式二之间来回切换， 第二汽缸固定为模式二； e )第一汽缸固定为模式二， 第二汽缸在模式一和模式二之间来回切换； f ) 第一汽缸以模式一运行和模式三的切换， 第二汽缸固定为模式二； g )第一汽缸固定为模式二， 第二汽缸以模式一运行和模式三的切换； 其中， 压缩机停机， 采用模式一将运行中的汽缸切换到模式二后停机， 此 时电源关闭， 接着压缩机启动， 将汽缸保持在模式二的状态启动， 此时电源打 开， 然后压缩机运行加速稳定后， 再切换到模式一运行的过程为模式三。  d) the first cylinder switches back and forth between mode one and mode two, the second cylinder is fixed to mode two; e) the first cylinder is fixed to mode two, and the second cylinder is switched back and forth between mode one and mode two; f) The first cylinder is switched between mode one mode and mode three, the second cylinder is fixed to mode two; g) the first cylinder is fixed to mode two, and the second cylinder is switched by mode one mode and mode three; wherein, the compressor is stopped, In mode 1, the running cylinder is switched to mode 2 and then stopped. At this time, the power is turned off, then the compressor is started, and the cylinder is kept in the mode 2 state. At this time, the power is turned on, and then the compressor is running stably, then switching. The process of running to mode one is mode three.
2.根据权利要求 1所述的旋转压缩机的控制方法， 其特征是所述的旋转压 缩机的外循环管路上设置有高低压力差维持装置， 该维持装置设置在空调、 冷 冻机或热水器***中。  2. The control method of a rotary compressor according to claim 1, wherein said external circulation line of said rotary compressor is provided with a high and low pressure difference maintaining means, and said maintaining means is provided in an air conditioner, a freezer or a water heater system in.
3.根据杈利要求 1所述的旋转压缩机的控制方法， 其特征是所述的控制方 法适用于变频压缩机。  3. The control method of a rotary compressor according to claim 1, wherein the control method is applied to an inverter compressor.
PCT/CN2008/000225 2007-02-04 2008-01-30 A controlling method of a rotary compressor WO2008101387A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CNA2007100267864A CN101012833A (en) 2007-02-04 2007-02-04 Control method of rotary compressor
CN200710026786.4 2007-02-04

Publications (1)

Publication Number Publication Date
WO2008101387A1 true WO2008101387A1 (en) 2008-08-28

Family

ID=38700524

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2008/000225 WO2008101387A1 (en) 2007-02-04 2008-01-30 A controlling method of a rotary compressor

Country Status (2)

Country Link
CN (1) CN101012833A (en)
WO (1) WO2008101387A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3150758A4 (en) * 2014-05-29 2017-11-29 Qingdao Haier Drum Washing Machine Co., Ltd. Heat pump clothes dryer with dual-exhaust compressor system and control method thereof

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101012833A (en) * 2007-02-04 2007-08-08 美的集团有限公司 Control method of rotary compressor
JP2010163927A (en) * 2009-01-14 2010-07-29 Toshiba Carrier Corp Multicylinder rotary compressor and refrigerating cycle apparatus
CN102032187A (en) * 2009-09-30 2011-04-27 广东美芝制冷设备有限公司 Control method and application of cold energy variable type rotary compressor
CN106704189A (en) * 2015-08-10 2017-05-24 珠海格力节能环保制冷技术研究中心有限公司 Compressor and heat exchange system
CN109269039B (en) * 2018-08-06 2020-11-10 珠海格力电器股份有限公司 Control method of compressor and refrigerant circulating system
CN109269052B (en) * 2018-09-20 2019-06-25 珠海格力电器股份有限公司 Air-conditioning system and its control method
CN112746960A (en) * 2019-10-30 2021-05-04 广东美芝制冷设备有限公司 Compressor and refrigeration cycle device with same
CN116293975A (en) * 2023-03-01 2023-06-23 青岛海信日立空调***有限公司 Air conditioning system

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1590769A (en) * 2003-09-02 2005-03-09 东芝开利株式会社 Air conditioner
CN1707115A (en) * 2004-06-08 2005-12-14 三星电子株式会社 Capacity varying device for rotary compressor
WO2005121558A1 (en) * 2004-06-11 2005-12-22 Toshiba Carrier Corporation Hermetic rotary compressor
WO2006014086A1 (en) * 2004-08-06 2006-02-09 Lg Electronics Inc. Capacity variable type rotary compressor and driving method thereof
WO2006016763A1 (en) * 2004-08-12 2006-02-16 Lg Electronics Inc. Capacity variable type twin rotary compressor and driving method thereof and airconditioner with this and driving method thereof
CN1890468A (en) * 2003-12-03 2007-01-03 东芝开利株式会社 Freezing cycle device
CN1904369A (en) * 2005-07-25 2007-01-31 乐金电子(天津)电器有限公司 Multisection rotating type compressor and airconditioner therefor
CN1924359A (en) * 2005-08-30 2007-03-07 上海日立电器有限公司 Capacity controlled compressor with one and two cylinders
CN101012833A (en) * 2007-02-04 2007-08-08 美的集团有限公司 Control method of rotary compressor

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1590769A (en) * 2003-09-02 2005-03-09 东芝开利株式会社 Air conditioner
CN1890468A (en) * 2003-12-03 2007-01-03 东芝开利株式会社 Freezing cycle device
CN1707115A (en) * 2004-06-08 2005-12-14 三星电子株式会社 Capacity varying device for rotary compressor
WO2005121558A1 (en) * 2004-06-11 2005-12-22 Toshiba Carrier Corporation Hermetic rotary compressor
WO2006014086A1 (en) * 2004-08-06 2006-02-09 Lg Electronics Inc. Capacity variable type rotary compressor and driving method thereof
WO2006016763A1 (en) * 2004-08-12 2006-02-16 Lg Electronics Inc. Capacity variable type twin rotary compressor and driving method thereof and airconditioner with this and driving method thereof
CN1904369A (en) * 2005-07-25 2007-01-31 乐金电子(天津)电器有限公司 Multisection rotating type compressor and airconditioner therefor
CN1924359A (en) * 2005-08-30 2007-03-07 上海日立电器有限公司 Capacity controlled compressor with one and two cylinders
CN101012833A (en) * 2007-02-04 2007-08-08 美的集团有限公司 Control method of rotary compressor

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3150758A4 (en) * 2014-05-29 2017-11-29 Qingdao Haier Drum Washing Machine Co., Ltd. Heat pump clothes dryer with dual-exhaust compressor system and control method thereof
US10633784B2 (en) 2014-05-29 2020-04-28 Qingdao Jiaonan Haier Washing Machine Co., Ltd. Heat pump dryer with dual-exhaust compressor system and control method thereof

Also Published As

Publication number Publication date
CN101012833A (en) 2007-08-08

Similar Documents

Publication Publication Date Title
WO2008101387A1 (en) A controlling method of a rotary compressor
CN101688536B (en) Rotary compressor and refrigeration cycle device
TWI223054B (en) Refrigeration system and method of controlling a refrigeration system
US20080003123A1 (en) Capacity Varying Type Rotary Compressor
EP1851434A1 (en) Capacity varying type rotary compressor and refrigeration system having the same
CN101091062A (en) Capacity varying type rotary compressor and refrigeration system having the same
CN1193199C (en) Air conditioning system with two compressors and method for operating the same
US20080120985A1 (en) Rotary compressor, control method thereof, and air conditioner using the same
EP3115611B1 (en) Two-stage rotary compressor and refrigerating circulation device having same
JP2001091071A (en) Multi-stage compression refrigerating machine
CN101122290A (en) Screw compressor
US20220010796A1 (en) Rotary compressor and refrigeration cycle device
KR20100023632A (en) Variable capacity type rotary compressor and refrigerator having the same and method for driving thereof
WO2015051537A1 (en) Refrigeration circulation apparatus
JP4991255B2 (en) Refrigeration cycle equipment
JP2699723B2 (en) Two-stage compression refrigeration system with check valve device
CN102713156B (en) Volume type expander and refrigeration cycle device using the volume type expander
JP5971633B2 (en) Refrigeration cycle equipment
JPWO2014064974A1 (en) Rotary compressor
JP2013096602A (en) Refrigeration cycle device
JP2004324595A (en) Positive displacement fluid machine
JP2001289189A (en) Two-stage compressible refrigerant compressor
JP2012247097A (en) Refrigerating cycle apparatus
JPH1026425A (en) Refrigerant compressor driving at variable speed and refrigeration cycle device provided with the same refrigerant compressor
CN110671833A (en) Compressor and refrigerating system

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 08706421

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 08706421

Country of ref document: EP

Kind code of ref document: A1