WO2021047247A1 - 双级压缩机及双级压缩机的控制方法及空调机组 - Google Patents

双级压缩机及双级压缩机的控制方法及空调机组 Download PDF

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Publication number
WO2021047247A1
WO2021047247A1 PCT/CN2020/098925 CN2020098925W WO2021047247A1 WO 2021047247 A1 WO2021047247 A1 WO 2021047247A1 CN 2020098925 W CN2020098925 W CN 2020098925W WO 2021047247 A1 WO2021047247 A1 WO 2021047247A1
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Prior art keywords
stage
compressor
pressure
compression
volume ratio
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PCT/CN2020/098925
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English (en)
French (fr)
Inventor
刘华
张治平
龙忠铿
李日华
毕雨时
武晓昆
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珠海格力电器股份有限公司
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Priority to US17/627,001 priority Critical patent/US20220268280A1/en
Publication of WO2021047247A1 publication Critical patent/WO2021047247A1/zh

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    • 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
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/02—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for several pumps connected in series or in parallel
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F04C28/12—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F04C28/12—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves
    • F04C28/125—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves with sliding valves controlled by the use of fluid other than 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/05—Speed
    • F04C2270/052—Speed angular
    • F04C2270/0525—Controlled or regulated
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/21—Pressure difference
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/08—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the rotational speed

Definitions

  • the present disclosure is based on the application with the CN application number 201910860820.0 and the filing date of September 11, 2019, and claims its priority.
  • the disclosure of the CN application is hereby incorporated into the present disclosure as a whole.
  • the present disclosure relates to the technical field of compressors, in particular to a two-stage compressor and a control method of the two-stage compressor and an air conditioning unit.
  • a capacity adjustment mechanism Under some conditions, when the unit is operating at a small load, the capacity adjustment mechanism is usually used to control the movement of the compressor's slider and change the compressor's capacity to meet demand.
  • the compressor In a two-stage compressor, the compressor is generally adjusted by frequency conversion to change the compressor capacity, but this method cannot effectively adjust the internal volume ratio of the two-stage compressor.
  • the compressor's compression end pressure and discharge pressure When they are not equal, over-compression and under-compression will occur. These two situations will cause additional energy loss and also produce strong periodic exhaust noise.
  • a two-stage compressor includes a low-pressure stage; a high-pressure stage, which is connected in series with the low-pressure stage; and a volume ratio adjustment mechanism, located in the high-pressure stage, configured to adjust the volume ratio of the high-pressure stage to the compression of refrigerant .
  • the compressor is a screw compressor
  • the volume ratio adjusting mechanism includes a first spool valve adjusting mechanism
  • the first spool valve adjusting mechanism is configured to adjust the output position of the exhaust port of the high pressure stage.
  • the two-stage compressor further includes a capacity adjustment mechanism, which is located in the low-pressure stage and is configured to adjust the output capacity of the low-pressure stage for refrigerant compression.
  • the capacity adjustment mechanism includes a second spool valve adjustment mechanism configured to adjust the output of the bypass port of the low pressure stage.
  • the capacity adjustment mechanism includes a plunger adjustment mechanism, and the plunger adjustment mechanism is configured to achieve volume adjustment by bypassing the intake air volume at a fixed point.
  • the capacity adjusting mechanism includes a rotational speed adjusting mechanism, and the rotational speed adjusting mechanism is configured to realize the capacity adjustment by changing the rotational speed of the motor to control the intake volume.
  • the two-stage compressor further includes a first driving mechanism connected to the first spool valve adjusting mechanism and configured to drive the first spool valve adjusting mechanism to move.
  • the two-stage compressor further includes a second driving mechanism connected to the second spool valve adjusting mechanism and configured to drive the second spool valve adjusting mechanism to move.
  • the present disclosure also provides a two-stage compressor control method for controlling the above-mentioned compressor.
  • the control method includes: when the compression end pressure of the compressor is less than the discharge pressure, the operating volume is increased by the adjusting mechanism to increase the high-pressure stage The volume ratio of the refrigerant compression; when the compression end pressure of the compressor is greater than the discharge pressure, the volume ratio adjustment mechanism is operated to reduce the volume ratio of the high-pressure stage to the refrigerant compression.
  • the present disclosure also provides an air conditioning unit, including the above-mentioned two-stage compressor.
  • the volume ratio adjustment mechanism when the compression end pressure of the compressor is less than the discharge pressure, the volume ratio adjustment mechanism is operated to increase the volume ratio of the high pressure stage to the refrigerant compression, so that the compression end pressure of the compressor is equal to the discharge pressure;
  • the operating volume ratio adjustment mechanism reduces the volume ratio of the high-pressure stage to the refrigerant compression, so that the compressor's final compression pressure is equal to the discharge pressure, and the compressor overcompression and undercompression are improved. In order to adapt to changes in external conditions, improve the energy efficiency of the compressor and reduce the noise of the compressor.
  • Fig. 1 is a schematic diagram of the overall structure of a two-stage compressor according to some embodiments of the present disclosure
  • Fig. 2 is a schematic structural diagram of the high-pressure stage of the two-stage compressor shown in Fig. 1;
  • Fig. 3 is a structural schematic diagram of the low-pressure stage of the two-stage compressor shown in Fig. 1.
  • Some embodiments of the present disclosure provide a two-stage compressor, a two-stage compressor control method, and an air conditioning unit, so as to solve the problem of the two-stage compressor in the related art due to the unequal compression end pressure of the compressor and the discharge pressure.
  • the final compression pressure of the compressor is the final compression pressure of the last stage of the compressor, which is the high-pressure stage.
  • FIG. 1 shows a two-stage compressor provided by some embodiments of the present disclosure.
  • the two-stage compressor includes a low-pressure stage 10 and a high-pressure stage 20 connected in series with the low-pressure stage 10.
  • the two-stage compressor further includes a volume ratio adjustment mechanism 30 provided in the high pressure stage 20, and the volume ratio adjustment mechanism 30 is configured to adjust the volume ratio of the high pressure stage 20 to the compression of the refrigerant.
  • the operating volume ratio adjusting mechanism 30 increases the volume ratio of the high pressure stage 20 to the refrigerant compression, so that the compression end pressure and the discharge pressure of the compressor Equal; when the compressor's final compression pressure is greater than the discharge pressure, the operating volume ratio adjusting mechanism 30 reduces the volume ratio of the high-pressure stage 20 to the refrigerant compression, so that the compressor's final compression pressure is equal to the discharge pressure and improves the compressor performance
  • the conditions of compression and under-compression can adapt to changes in external conditions, improve the energy efficiency of the compressor, and reduce the noise of the compressor.
  • the compressor is a screw compressor
  • the volume ratio adjustment mechanism 30 includes a first spool valve adjustment mechanism, which is configured to adjust the discharge port 21 of the high pressure stage. Output location.
  • refrigerants with different volume ratios are discharged from the high-pressure stage 20.
  • the slide valve of the first slide valve adjustment mechanism moves to the suction side of the screw compressor (the left side shown in Figure 2).
  • the output position of the exhaust port 21 of the high pressure stage is toward the screw compressor.
  • the suction side moves to reduce the pressure at the end of compression of the high pressure stage 20, so that the pressure at the end of compression of the high pressure stage 20 is equal to the discharge pressure.
  • the form of the volume ratio adjustment mechanism 30 is not limited to the spool valve adjustment mechanism.
  • the two-stage compressor further includes a bearing 80 for setting the rotor of the low-pressure stage 10 and the rotor of the high-pressure stage 20, and a motor 70 that drives the rotor of the low-pressure stage 10 and the high-pressure stage 20 to rotate.
  • the two-stage compressor further includes a capacity adjustment mechanism 40.
  • the capacity adjustment mechanism 40 is provided in the low-pressure stage 10 and is configured to adjust the output capacity of the low-pressure stage 10 for refrigerant compression.
  • the two-stage compressor has both capacity adjustment and internal volume ratio adjustment functions. The two-stage compressor can not only adjust the capacity of the compressor according to external requirements to meet the needs of different load operation; at the same time, it can also adjust the internal volume ratio according to external pressure changes, change the compressor's end-of-compression pressure, and avoid compressor over-compression. And under-compression to reduce noise and improve compressor energy efficiency.
  • the capacity adjustment and inner volume ratio adjustment of the two-stage compressor are used separately.
  • the capacity adjustment mechanism 40 includes a second spool valve adjustment mechanism configured to adjust the output of the bypass port 11 of the low pressure stage 10.
  • the bypass port 11 of the low pressure stage 10 is closed, and the compressor is in a full load state.
  • the system moves to the exhaust side (the right side shown in Figure 3) by adjusting the slide valve of the second slide valve adjustment mechanism.
  • the bypass port 11 of the low pressure stage 10 and the suction side Connected that is, the partially compressed gas is bypassed to the suction side, and the actual suction volume is changed, so that the capacity adjustment function can be realized.
  • the volume adjustment mechanism 40 may also be selected as a plunger adjustment mechanism, which is used to achieve volume adjustment through a fixed-point bypass suction volume.
  • the capacity adjustment mechanism 40 may also be a rotation speed adjustment mechanism, and the rotation speed adjustment mechanism realizes the capacity adjustment by changing the motor rotation speed to control the air intake.
  • the capacity adjustment mechanism 40 includes a frequency converter, but the speed adjustment mechanism is not limited to include a frequency converter.
  • the two-stage compressor further includes a first driving mechanism 50 connected to the first spool valve adjusting mechanism and used to drive the first spool valve adjusting mechanism to move.
  • the two-stage compressor further includes a second drive mechanism 60 connected to the second spool valve adjustment mechanism for driving the second spool valve adjustment mechanism to move.
  • both the first driving mechanism 50 and the second driving mechanism 60 include a movable cylinder, and the output end of the movable cylinder is connected with the first spool valve adjusting mechanism or the second spool valve adjusting mechanism to realize that the movable cylinder drives the first The spool valve adjustment mechanism or the second spool valve adjustment mechanism moves.
  • the movable cylinder is a hydraulic cylinder or an air cylinder or an electric cylinder.
  • the above embodiment is an example of selecting one form of capacity adjustment and internal volume ratio adjustment.
  • the single-machine two-stage screw compressor of the present disclosure may also adopt other forms that can realize capacity adjustment and internal volume ratio adjustment.
  • the present disclosure also provides a two-stage compressor control method, which is used to control the above-mentioned two-stage compressor, and the control method includes:
  • the volume ratio adjusting mechanism 30 is operated to increase the volume ratio of the high pressure stage of the compressor to the refrigerant compression
  • the volume ratio adjusting mechanism 30 When the compression end pressure of the compressor is greater than the discharge pressure, the volume ratio adjusting mechanism 30 is operated to reduce the volume ratio of the high pressure stage of the compressor to the compression of the refrigerant.
  • the compressor When the compressor is running, when the discharge pressure changes, the compressor's final compression pressure is not equal to the discharge pressure. At this time, over-compression and under-compression will occur, causing the compressor to make noise and consume a lot of power. . Therefore, at this time, the compressor will detect and compare the end pressure of the compressor with the discharge pressure, and compare the pressure to determine the pressure relationship, and give an instruction for the movement direction of the output position of the high-pressure stage exhaust port. When it is detected that the end pressure of the compressor is not equal to the discharge pressure, the discharge pressure of the high-pressure stage 20 is adjusted to achieve the purpose of changing the end pressure of the compressor.
  • the volume ratio adjustment mechanism 30 When the compression end pressure of the compressor is less than the discharge pressure, the volume ratio adjustment mechanism 30 is operated to increase the volume ratio of the high-pressure stage 20 to the refrigerant compression; when the compression end pressure of the compressor is greater than the discharge pressure, the volume ratio adjustment mechanism 30 is operated Reduce the volume ratio of the high-pressure stage 20 to the refrigerant compression.
  • the position of the exhaust port moves forward, so that the compression end pressure of the high-pressure stage 20 is reduced, thereby causing the compression
  • the end pressure of the compressor is equal to the exhaust pressure.
  • the present disclosure also provides an air conditioning unit, including the above-mentioned two-stage compressor.
  • the use of the above-mentioned two-stage compressor can improve the energy efficiency of the air conditioning unit.

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

Abstract

一种双级压缩机及双级压缩机的控制方法及空调机组。该双级压缩机包括低压级（10）和与低压级（10）串联的高压级（20），以及容积比调节机构（30），设于高压级（20），用于调节高压级（20）对冷媒压缩的容积比。当压缩机的压缩终了压力小于排气压力时，操作容积比调节机构（30）增大高压级（20）对冷媒压缩的容积比，从而使压缩机的压缩终了压力与排气压力相等；当压缩机的压缩终了压力大于排气压力时，操作容积比调节机构（30）降低高压级（20）对冷媒压缩的容积比，从而使压缩机的压缩终了压力与排气压力相等。改善过压缩和欠压缩的情况，以适应外界条件变化，提高压缩机的能效，降低压缩机噪音。

Description

双级压缩机及双级压缩机的控制方法及空调机组
相关申请的交叉引用
本公开是以CN申请号为201910860820.0，申请日为2019年9月11日的申请为基础，并主张其优先权，该CN申请的公开内容在此作为整体引入本公开中。
技术领域
本公开涉及压缩机技术领域，尤其涉及一种双级压缩机及双级压缩机的控制方法及空调机组。
背景技术
相关单级压缩机包括容量调节机构，在一些条件下，机组运行较小负荷工况时，通常采用容量调节机构控制压缩机的滑块移动，改变压缩机的容量，以满足需求。
在双级压缩机中，一般采用对压缩机进行变频调节的方式来改变压缩机的容量，但该方式不能有效调节双级压缩机的内容积比，当压缩机的压缩终了压力和排气压力不相等时，会出现过压缩和欠压缩的情况，这两种情况会造成附加的能量损失，也会产生强烈的周期性排气噪音。
发明内容
依据本公开的一些实施例的一个方面，双级压缩机包括低压级；高压级，与低压级串联；以及容积比调节机构，设于高压级，被配置为调节高压级对冷媒压缩的容积比。
在一些实施例中，压缩机为螺杆压缩机，容积比调节机构包括第一滑阀调节机构，第一滑阀调节机构被配置为调节高压级的排气口的输出位置。
在一些实施例中，双级压缩机还包括容量调节机构，设于低压级，被配置为调节低压级对冷媒压缩的输出容量。
在一些实施例中，容量调节机构包括第二滑阀调节机构，第二滑阀调节机构被配置为调节低压级的旁通口的输出量。
在一些实施例中，容量调节机构包括柱塞调节机构，柱塞调节机构被配置为通过定点旁通吸气量实现容量调节。
在一些实施例中，容量调节机构包括转速调节机构，转速调节机构被配置为通过 改变电机转速控制吸气量实现容量调节。
在一些实施例中，双级压缩机还包括第一驱动机构，第一驱动机构与第一滑阀调节机构相连，被配置为驱动第一滑阀调节机构运动。
在一些实施例中，双级压缩机还包括第二驱动机构，第二驱动机构与第二滑阀调节机构相连，被配置为驱动第二滑阀调节机构运动。
本公开还提供了一种双级压缩机的控制方法，用于控制上述的压缩机，该控制方法包括：当压缩机的压缩终了压力小于排气压力时，操作容积比调节机构增大高压级对冷媒压缩的容积比；当压缩机的压缩终了压力大于排气压力时，操作容积比调节机构降低高压级对冷媒压缩的容积比。
本公开还提供了一种空调机组，包括上述的双级压缩机。
在上述实施例中，当压缩机的压缩终了压力小于排气压力时，操作容积比调节机构增大高压级对冷媒压缩的容积比，从而使压缩机的压缩终了压力与排气压力相等；当压缩机的压缩终了压力大于排气压力时，操作容积比调节机构降低高压级对冷媒压缩的容积比，从而使压缩机的压缩终了压力与排气压力相等，改善压缩机过压缩和欠压缩的情况，以适应外界条件变化，提高压缩机的能效，降低压缩机噪音。
附图说明
图1是根据本公开一些实施例提供的双级压缩机的整体结构示意图；
图2是图1所示的双级压缩机的高压级的结构示意图；
图3是图1所示的双级压缩机的低压级的结构示意图。
具体实施方式
下面将结合本公开实施例中的附图，对实施例中的技术方案进行清楚、完整地描述。显然，所描述的实施例仅仅是本公开的一部分实施例，而不是全部的实施例。基于本公开的实施例，本领域普通技术人员在没有作出创造性劳动前提下所获得的所有其他实施例，都属于本公开保护的范围。
在本公开的描述中，需要理解的是，术语“中心”、“纵向”、“横向”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”、“内”、“外”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本公开和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本公开保护范围的限制。
本公开的一些实施例提供了一种双级压缩机及双级压缩机的控制方法及空调机 组，以解决相关技术中双级压缩机存在的由于压缩机的压缩终了压力和排气压力不相等所造成的能量损失及噪音的技术问题。
压缩机的压缩终了压力为压缩机的最后一级也就是高压级的压缩终了压力。
图1示出了本公开一些实施例提供的双级压缩机，该双级压缩机包括低压级10和与低压级10串联的高压级20。双级压缩机还包括容积比调节机构30，设于高压级20，容积比调节机构30被配置为调节高压级20对冷媒压缩的容积比。
应用本公开的技术方案，当压缩机的压缩终了压力小于排气压力时，操作容积比调节机构30增大高压级20对冷媒压缩的容积比，从而使压缩机的压缩终了压力与排气压力相等；当压缩机的压缩终了压力大于排气压力时，操作容积比调节机构30降低高压级20对冷媒压缩的容积比，从而使压缩机的压缩终了压力与排气压力相等，改善压缩机过压缩和欠压缩的情况，以适应外界条件变化，提高压缩机的能效，降低压缩机噪音。
在一些实施例中，如图2所示，压缩机为螺杆压缩机，容积比调节机构30包括第一滑阀调节机构，第一滑阀调节机构被配置为调节高压级的排气口21的输出位置。通过改变高压级的排气口21的输出位置，使得不同容积比的冷媒从高压级20排出。例如：高压级的排气口21的输出位置越靠近螺杆压缩机的吸气侧，冷媒的容积比越低，高压级的排气口21的输出位置越靠近螺杆压缩机的排气侧，冷媒的容积比越高。在使用时，第一滑阀调节机构的滑阀向螺杆压缩机的吸气侧(图2中所示的左侧)移动，此时高压级的排气口21的输出位置向螺杆压缩机的吸气侧移动，使高压级20压缩终了压力降低，从而使高压级20压缩终了压力与排气压力相等。通过控制第一滑阀调节机构的滑阀至设定位置，改变高压级20的内容积比，以使压缩机的压缩终了压力与排气压力匹配，以降低压缩机噪音，提高压缩机能效。
作为其他的可选的实施方式，容积比调节机构30的形式也不限于滑阀调节机构。
在一些实施例中，如图1所示，双级压缩机还包括架设低压级10转子和高压级20转子的轴承80以及驱动低压级10转子和高压级20转子转动的电机70。
如图1和图3所示，在一些实施例中，双级压缩机还包括容量调节机构40，容量调节机构40设于低压级10，被配置为调节低压级10对冷媒压缩的输出容量。在一些实施例中，双级压缩机同时具备容量调节和内容积比调节的功能。该双级压缩机不仅可以根据外界需求，调节压缩机的容量，满足不同负荷运行的需求；同时还可以根据外界压力变化，调节内容积比，改变压缩机的压缩终了压力，避免压缩机过压缩和欠压缩的情况，以降低噪音、提高压缩机能效。
在一些实施例中，双级压缩机的容量调节和内容积比调节是单独使用的。
在一些实施例中，如图3所示，容量调节机构40包括第二滑阀调节机构，第二滑阀调节机构被配置为调节低压级10的旁通口11的输出量。当第二滑阀调节机构的滑阀的前端与挡块12完全接触时，此时低压级10的旁通口11闭合，压缩机处于满负荷状态。当有部分负荷运行需求时，系统通过调节第二滑阀调节机构的滑阀向排气侧(图3中所示的右侧)移动，此时低压级10的旁通口11与吸气侧连通，即部分压缩后的气体旁通至吸气侧，实际吸气量改变，如此可实现容量调节功能。
作为其他的可选的实施方式，容量调节机构40也可以选择为柱塞调节机构，柱塞调节机构用于通过定点旁通吸气量实现容量调节。
作为另一种可选的实施方式，容量调节机构40也可以为转速调节机构，转速调节机构通过改变电机转速控制吸气量实现容量调节。可选的，在本实施例的技术方案中，容量调节机构40包括变频器，但转速调节机构也不仅限于包括变频器。
在一些实施例中，双级压缩机还包括第一驱动机构50，第一驱动机构50与第一滑阀调节机构相连，用于驱动第一滑阀调节机构运动。
在一些实施例中，双级压缩机还包括第二驱动机构60，第二驱动机构60与第二滑阀调节机构相连，用于驱动第二滑阀调节机构运动。
可选的，第一驱动机构50和第二驱动机构60均包括活动缸，将活动缸的输出端与第一滑阀调节机构或第二滑阀调节机构连接，即可实现活动缸驱动第一滑阀调节机构或第二滑阀调节机构运动。可选的，活动缸为液压缸或气缸或电动缸。
如上实施方式为选择容量调节和内容积比调节其中的一种形式进行举例，本公开的单机双级螺杆压缩机也可以采用其他可以实现容量调节和内容积比调节的形式。
在压缩机运行时，当排气压力发生变化后，压缩机的压缩终了压力与排气压力不相等，此时会出现过压缩机压缩和欠压缩的情况，造成压缩机噪音大，耗功多的问题。
本公开还提供了一种双级压缩机的控制方法，用于控制上述的双级压缩机，该控制方法包括：
当压缩机的压缩终了压力小于排气压力时，操作容积比调节机构30增大压缩机高压级对冷媒压缩的容积比；
当压缩机的压缩终了压力大于排气压力时，操作容积比调节机构30降低压缩机高压级对冷媒压缩的容积比。
当压缩机运行时，当排气压力发生变化后，压缩机的压缩终了压力与排气压力不相等，此时会出现过压缩和欠压缩的情况，造成压缩机噪音大，耗功多的问题。所以此时压缩机会检测对比压缩机压缩终了压力与排气压力，并进行对比，判断压力关系，给出高压级排气口输出位置的移动方向的指令。当检测到压缩机的压缩终了压力与排 气压力不相等时，调节高压级20的排气压力，以达到改变压缩机压缩终了压力的目的。当压缩机的压缩终了压力小于排气压力时，操作容积比调节机构30增大高压级20对冷媒压缩的容积比；当压缩机的压缩终了压力大于排气压力时，操作容积比调节机构30降低高压级20对冷媒压缩的容积比。
可选的，如图2所示，结合上述的滑阀调节机构的实施方式，当高压级压缩终了压力小于排气压力时，下达指令至第一滑阀调节机构，使滑阀往排气侧(右侧)移动，此时排气孔口位置后移，使高压级20的压缩终了压力增大，从而使压缩机的压缩终了压力与排气压力相等；当压缩机的压缩终了压力大于排气压力时，下达指令至第一滑阀调节机构，使滑阀往吸气侧(左侧)移动，此时排气孔口位置前移，使高压级20的压缩终了压力降低，从而使压缩机的压缩终了压力与排气压力相等。通过控制第一滑阀调节机构的滑阀移动至设定位置，改变高压级的内容积比，使压缩机的压缩终了压力与排气压力匹配，以降低压缩机噪音，提高压缩机能效。
应用本公开的技术方案，当外界压力发生变化时，可通过检测压缩机的压缩终了压力与排气压力，判断二者关系并下达指令至内容积比调节结构，调节高压级排气孔口位置，使得压缩终了压力与排气压力相近，改善过压缩和欠压缩的情况，以适应外界条件变化，提高压缩机的能效，降低压缩机噪音。
本公开还提供了一种空调机组，包括上述的双级压缩机。采用上述的双级压缩机，可以提高空调机组的能效。
在本公开的描述中，需要理解的是，使用“第一”、“第二”等词语来限定零部件，仅仅是为了便于对上述零部件进行区别，如没有另行声明，上述词语并没有特殊含义，因此不能理解为对本公开保护范围的限制。
最后应当说明的是:以上实施例仅用以说明本公开的技术方案而非对其限制；尽管参照较佳实施例对本公开进行了详细的说明，所属领域的普通技术人员应当理解：依然可以对本公开的具体实施方式进行修改或者对部分技术特征进行等同替换；而不脱离本公开技术方案的精神，其均应涵盖在本公开请求保护的技术方案范围当中。

Claims (10)

  1. 一种双级压缩机，包括：
    低压级(10)；
    高压级(20)，与所述低压级(10)串联；以及
    容积比调节机构(30)，设于所述高压级(20)，被配置为调节所述高压级(20)对冷媒压缩的容积比。
  2. 根据权利要求1所述的双级压缩机，其中，所述压缩机为螺杆压缩机，所述容积比调节机构(30)包括第一滑阀调节机构，所述第一滑阀调节机构被配置为调节所述高压级(20)的排气口(21)的输出位置。
  3. 根据权利要求1述的双级压缩机，还包括容量调节机构(40)，设于所述低压级(10)，被配置为调节所述低压级(10)对冷媒压缩的输出容量。
  4. 根据权利要求3所述的双级压缩机，其中，所述容量调节机构(40)包括第二滑阀调节机构，所述第二滑阀调节机构被配置为调节所述低压级(10)的旁通口(11)的输出量。
  5. 根据权利要求3所述的双级压缩机，其中，所述容量调节机构(40)包括柱塞调节机构，所述柱塞调节机构被配置为通过定点旁通吸气量实现容量调节。
  6. 根据权利要求3所述的双级压缩机，其中，所述容量调节机构(40)包括转速调节机构，所述转速调节机构被配置为通过改变电机转速控制吸气量实现容量调节。
  7. 根据权利要求2所述的双级压缩机，其中，所述双级压缩机还包括第一驱动机构(50)，所述第一驱动机构(50)与所述第一滑阀调节机构相连，被配置为驱动所述第一滑阀调节机构运动。
  8. 根据权利要求4所述的双级压缩机，其中，所述双级压缩机还包括第二驱动机构(60)，所述第二驱动机构(60)与所述第二滑阀调节机构相连，被配置为驱动所述第二滑阀调节机构运动。
  9. 一种双级压缩机的控制方法，用于控制权利要求1至8中任一项所述的压缩机，所述控制方法包括：
    当所述压缩机的压缩终了压力小于排气压力时，操作所述容积比调节机构(30)增大所述高压级(20)对冷媒压缩的容积比；
    当所述压缩机的压缩终了压力大于排气压力时，操作所述容积比调节机构(30)降低所述高压级(20)对冷媒压缩的容积比。
  10. 一种空调机组，包括如权利要求1至8中任一项所述的双级压缩机。
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