WO2015010502A1 - 一种装有能效增大器的蒸气压缩式空调系统 - Google Patents

一种装有能效增大器的蒸气压缩式空调系统 Download PDF

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Publication number
WO2015010502A1
WO2015010502A1 PCT/CN2014/078951 CN2014078951W WO2015010502A1 WO 2015010502 A1 WO2015010502 A1 WO 2015010502A1 CN 2014078951 W CN2014078951 W CN 2014078951W WO 2015010502 A1 WO2015010502 A1 WO 2015010502A1
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WIPO (PCT)
Prior art keywords
energy efficiency
air conditioning
bellows
conditioning system
vapor compression
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Application number
PCT/CN2014/078951
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English (en)
French (fr)
Inventor
陈恩鉴
徐晓丽
王显龙
Original Assignee
余伟俊
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Publication date
Application filed by 余伟俊 filed Critical 余伟俊
Publication of WO2015010502A1 publication Critical patent/WO2015010502A1/zh
Priority to US14/963,242 priority Critical patent/US9897358B2/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B45/00—Arrangements for charging or discharging refrigerant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers

Definitions

  • the invention belongs to the technical field of refrigeration and heating, and particularly relates to a vapor compression heat pump air conditioning system equipped with an energy efficiency increaser. Background technique
  • the vapor compression air conditioning system includes an air conditioning refrigeration-heat pump system, a simple air conditioning refrigeration system, a simple heat pump system, and a heat pump water heater system.
  • the essence of the working process is that the working medium is compressed after being extracted from a low temperature medium (such as indoor or outdoor air).
  • the machine compresses and raises the temperature to release heat to a high temperature medium such as outdoor or indoor air.
  • the condensing temperature of the working fluid should be higher than the temperature of the high temperature medium by a minimum reasonable temperature difference A Tk
  • the evaporation temperature of the working medium should be lower than the temperature of the low temperature medium by a minimum reasonable temperature difference ⁇ ⁇ .
  • the existing air conditioning refrigeration-heat pump system responds to changes in working conditions, and mainly has the following two performance adjustment methods:
  • Frequency conversion adjustment The frequency conversion adjustment mainly aims to change the flow rate of the working fluid and the power consumption of the compressor by changing the speed of the compressor. In this way, when the temperature is not too high, energy saving can be achieved by appropriately reducing the compressor speed.
  • Expansion valve adjustment including thermal expansion valve and electronic expansion valve.
  • the adjustment principle is to change the flow rate and expansion ratio of the working fluid by changing the throttle area of the expansion valve.
  • the above problems are particularly acute when the unit is switched between air conditioning refrigeration and heat pump operating conditions.
  • the external ambient temperature range is 27 °C (indoor) to 35 °C (outdoor); in winter heat pump operating conditions, the external temperature range is 20 °C (indoor) to 2
  • the traditional heat pump air conditioning system is designed to reduce the area of the indoor heat exchanger and increase the indoor heat exchange temperature difference.
  • the working fluid evaporation temperature during summer cooling will be reduced from 12 ° C to 5 V; while the winter heating temperature will increase from 35 ° C to 43 ° C.
  • the difference between the working temperature of the working medium in winter and summer will be reduced to about 1 CTC, and the difference in the optimum working fluid filling capacity can be reduced, but the cost is also reduced in design energy efficiency ratio. It will drop from 4 to 3.
  • the present invention proposes that the working volume side of the vapor compression air conditioning system is continuously adjustable.
  • the technical solution is to make the average density of the working medium in the system change from a fixed state to an adjustable state.
  • the change of the volume on the working side means that the average density of the working medium changes.
  • the average density of the circulating working medium increases, if the other conditions are constant, the condensation temperature and the evaporation temperature of the working medium cycle increase, and vice versa.
  • This provides a new means of adjustment for the operation of the air conditioning system, thereby effectively improving the energy efficiency ratio of the air conditioning system.
  • a vapor compression air conditioning system equipped with an energy efficiency augmenter comprising a compressor, a condenser, an expansion valve, an evaporator, and a pipeline sequentially connecting the above mechanisms a working fluid circulation loop, and an energy efficiency increaser is connected to the working fluid circulation loop, and the energy efficiency increaser package Includes a variable volume container and an actuator that changes the volume of the container.
  • system further includes a four-way valve.
  • the four-way valve When the four-way valve is connected in the working fluid circulation loop, the four-way valve is switched to operate the circulation circuit in an air conditioning refrigeration or heat pump mode.
  • the condenser is also connected to the water tank and the circulation pump through a pipe to form a water heating circulation circuit.
  • connection position of the variable volume container to the working fluid circulation circuit is set at the circulation line of the compressor outlet.
  • variable volume container is a bellows that is telescopically deformable, and two ends of the bellows are respectively closed by a bottom plate, and one end plate of the bellows is connected to a working medium circulation loop pipe through a connecting pipe, The other end plate of the bellows is connected to the actuator.
  • the actuator is composed of a nut screw moving pair, the outer circumference of the nut is a worm wheel, and the worm matched with the worm wheel is driven by a motor, and one end of the screw is fixedly connected with the bottom plate of the bellows.
  • the heat pump air conditioning system with the energy efficiency increaser of the invention can significantly improve the energy efficiency ratio of the system, so that the energy efficiency ratio of the working condition can reach about 4, and the seasonal energy efficiency ratio can exceed the energy efficiency ratio of the design working condition, and the air conditioning system is significantly improved. Running performance.
  • FIG. 1 is a schematic view of a simple air conditioning refrigeration system of Embodiment 1;
  • Figure 2 is a schematic view of Embodiment 2 - a simple heat pump system
  • Figure 3 is a schematic view of Embodiment 3 - heat pump water heater system
  • FIG. 4 is a schematic view of an air conditioning refrigeration-heat pump system of Embodiment 4.
  • Figure 5 is a schematic view of an embodiment of an energy efficiency increaser
  • Figure 6 is a cyclic temperature entropy plot of a system equipped with an energy efficiency augmenter. detailed description
  • Embodiment 1 is a schematic view of a simple air conditioning refrigeration system of Embodiment 1, including a compressor 1, a condenser (outdoor unit) 3, an expansion valve 4, an evaporator (indoor unit) 5, and a working medium composed of pipes sequentially connected to the above mechanisms. Loop circuit.
  • An energy efficiency increaser 6 is connected to the working fluid circulation loop, and the energy efficiency increaser is composed of a variable volume container 61 and a change container volume.
  • the executive body 62 is composed.
  • the connection position of the variable volume container 61 and the working fluid circulation circuit is set at the circulation pipe at the outlet of the compressor 1, because the circulating medium has high pressure, high density, and variable volume.
  • variable volume container can also be connected to other locations of the system loop, or multiple variable volume containers can be connected to the loop.
  • the condensing temperature of the working fluid When the outdoor temperature drops in summer, the condensing temperature of the working fluid also decreases. Correspondingly, the condensing pressure and density of the working fluid also decrease, and the quality of the circulating circuit is in an excessive state, which will lead to a decrease in the energy efficiency ratio.
  • the volume of the variable volume container 61 can be slightly enlarged, the average density of the working medium in the circulation loop can be reduced, and the quality of the work in the circulation loop can be optimized, and the system has the best energy efficiency ratio and refrigeration capacity.
  • the mass flow rate of the working medium passing through the compressor can also be adjusted, thereby realizing the variable capacity by using the constant speed conventional compressor.
  • the purpose of air conditioning. Therefore, the present invention has the potential to replace the inverter air conditioner.
  • FIG. 2 is a schematic view of the embodiment 2 - a simple heat pump system, including a compressor 1, a condenser (indoor unit) 3, an expansion valve 4, an evaporator (outdoor unit) 5, and a working fluid cycle consisting of pipes sequentially connected to the above mechanisms. Loop.
  • the energy efficiency booster 6 is connected to the working fluid circulation loop, and the energy efficiency booster is composed of a variable volume container 61 and an actuator 62 that changes the volume of the container.
  • the connection position of the variable volume container 61 and the working fluid circulation circuit is set at the circulation pipe at the outlet of the compressor 1, because the circulating medium has high pressure, high density, and variable volume.
  • variable volume container can also be connected to other locations of the system loop, or multiple variable volume containers can be connected to the loop.
  • variable volume container 61 When the outdoor temperature drops in winter, the volume of the variable volume container 61 can be slightly enlarged, and the average density of the working medium in the circulation circuit can be reduced. At this time, the evaporation temperature of the working medium will also decrease, so that the evaporator maintains a reasonable optimal transmission. The thermal temperature difference, at this time the system achieves high-efficiency heating at low temperatures without substantially reducing the energy efficiency ratio and heating capacity.
  • FIG. 3 is a schematic diagram of a heat pump water heater system equipped with an energy efficiency increaser, comprising a compressor 1, a condenser 3, an expansion valve 4, an evaporator 5, and a working fluid circulation circuit composed of pipes sequentially connected to the above mechanisms.
  • the condenser 3 is also connected to the water tank 7 and the circulation pump 8 Form a water heating circuit.
  • An energy efficiency increaser 6 is connected to the working fluid circulation loop, and the energy efficiency increaser is composed of a variable volume container 61 and an actuator 62 that changes the volume of the container.
  • the connection position of the variable volume container 61 and the working fluid circulation circuit is set at the circulation pipe at the outlet of the compressor 1, because the circulating medium has high pressure, high density, and variable volume.
  • variable volume container can also be connected to other locations of the system loop, or multiple variable volume containers can be connected to the loop.
  • the water temperature is gradually increased. For example, the water temperature at the beginning of heating is 10 ° C, and the temperature of the heated water is raised to 55 ° C. Therefore, the condensation temperature of the heat pump water heater should be correspondingly 25 °. C is increased to 65 °C. If the environmentally friendly working fluid 134a is used, the density of the gaseous working medium is 32 kg/m 3 at 25 °C, and the density of the gaseous working medium is 100 kg/m 3 at 65 °C, which is up to 3 times. The filling capacity of the conventional heat pump water heater is difficult to adapt to this situation. When the heating starts, the working medium is in a serious excess condition, and when the heating is finished, the working quality may be too low.
  • FIG. 4 is a schematic view of an air conditioning refrigeration-heat pump system of Embodiment 4, including a compressor 1, a four-way valve 2, a condenser 3, an expansion valve 4, an evaporator 5, and a working fluid circulation circuit composed of pipes sequentially connected to the above mechanisms. Switching the four-way valve 2 allows the circulation circuit to operate in an air conditioning refrigeration or heat pump mode.
  • the energy efficiency increaser 6 is connected to the working fluid circulation loop, and the energy efficiency booster is composed of a variable volume container 61 and an actuator 62 that changes the volume of the container.
  • the connection position of the variable volume container 61 and the working fluid circulation circuit is set at the circulation pipe at the outlet of the compressor 1, because the circulating medium has high pressure, high density, and variable volume.
  • variable volume container 61 can have a relatively large influence on the average density of the working medium in the system circulation loop, and the adjustment sensitivity is relatively high.
  • variable volume container can also be connected to other locations of the system loop, or multiple variable volume vessels can be connected to the loop.
  • the temperature of the variable volume container 61 can be increased to reduce the circulation loop when the temperature is switched to the heat pump condition (for example, the working medium condensation temperature is 35 ° C and the evaporation temperature is 10 ° C).
  • the average density of the working medium is such that the condensation temperature of the working medium is gradually reduced from 50 ° C to 35 ° C, and the evaporation temperature of the corresponding working medium is lowered from 12 ° C to about 10 ° C to realize the switching of working conditions.
  • the optimal energy efficiency ratio of the existing air conditioning system is increased by more than 10%.
  • the volume of the variable volume container 61 can be reduced to adapt the filling amount of the working medium to the change of the working temperature of the working medium.
  • the invention can realize the comprehensive and precise adjustment of the air-conditioning heat pump system if combined with the expansion valve regulation or the frequency conversion adjustment, so that the A Tk and the A Te can be adjusted to the optimum value under various working conditions at the same time.
  • the energy efficiency ratio will reach the maximum value under this condition.
  • Fig. 5 is a schematic view showing an embodiment of an energy efficiency augmenter of a vapor compression type air conditioning system equipped with an energy efficiency augmenter.
  • the variable volume container 61 is a bellows 611 which is telescopically deformable, and two ends of the bellows are respectively closed by a bottom plate, and one end bottom plate 612 of the bellows passes through a connecting pipe and a working medium circulation pipe. The other end of the bellows is connected to the actuator 62.
  • the actuator 62 is composed of a nut screw moving pair, the outer circle of the nut 621 is a worm wheel 623, and the worm 624 matched with the worm wheel is driven by a motor 625, and one end of the screw 622 is fixed to the bottom plate of the bellows. connection.
  • the motor 625 rotates or reverses
  • the worm nut 621 also rotates forward or reverse, thereby causing the lead screw 622 to move forward or backward, and the bottom plate 613 of the bellows container is moved to change the volume of the container.
  • a cylindrical body 615 is spliced inside the one end 613 of the bellows, the diameter of the cylinder is slightly smaller than the inner diameter of the bellows, and the length of the cylinder is slightly larger than when the bellows is completely compressed. length.
  • the inner diameter of the bellows is 20cm, and the diameter of the cylinder 615 is 19.8cm.
  • the length is
  • the length of the cylinder is 10.1 cm.
  • the distance between the end surface of the cylindrical body 614 and the inner end surface of the front bottom plate 613 varies from 0 to 15 cm, and the length of the corresponding bellows varies from 10 cm to 25 cm.
  • the energy efficiency increaser of the present invention may have other structural forms in addition to the bellows of the above embodiment and its mechanical drive mechanism, such as a piston type cylinder and a hydraulic drive mechanism, and the movement of the piston in the cylinder is driven by the hydraulic mechanism.
  • Can The variable volume container can also adopt a structure such as a bellows type or a special deformable composite material.
  • Figure 6 is a cyclic temperature entropy diagram of an air conditioning system equipped with an energy efficiency augmenter, wherein the abscissa S represents the entropy value and the ordinate T represents the temperature value.
  • the essence of the adjustment method of changing the volume of the working medium is to change the average density of the working medium participating in the circulation, so that the condensation temperature and the evaporation temperature of the working medium are simultaneously raised or lowered, and the closed curve represented by the solid line in the figure is 1-2- 3-4 is the cycle curve under the design condition, where 1-2 is the working medium compression process, 2-3 is the working medium condensation process, 3-4 is the working medium expansion process, and 4-1 is the working medium evaporation process.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Air Conditioning Control Device (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

一种蒸汽压缩式空调系统，在系统工质循环回路中装有能效增大器（6），该能效增大器（6）包括可变容积容器（61）和改变容器容积的执行机构（62）。该能效增大器（6）可利用可变容积容器（61）接收系统回路中的工质以改变工质的平均密度，从而使系统处于最佳能效比，改善空调系统的运行性能。

Description

一种装有能效增大器的蒸气压缩式空调系统
技术领域
本发明属于制冷制热技术领域，特别涉及一种装有能效增大器的 蒸气压缩式热泵空调系统。 背景技术
蒸气压缩式空调系统包括空调制冷一热泵系统、单纯空调制冷系统、 单纯热泵系统以及热泵热水器系统， 其工作过程的本质是其工质从低温 介质 （如室内或室外空气） 吸取热量后， 经压缩机压缩提高温度后向高 温介质（如室外或室内空气）放出热量。 为取得最经济高效的运行效果， 其工质的冷凝温度应比高温介质的温度高出一个最小的合理温差 A Tk， 而工质的蒸发温度应比低温介质的温度低一个最小合理温差 Δ ΤΘ。
在设计工况下， 上述的要求基本可以得到遵守，此时系统达到最佳 能效比和工作能力。 但在实际运行过程中往往不能到达上述理想要求。
现有的空调制冷一热泵系统为应对工况的变动， 主要有如下两种性 能调节手段：
1 ) 变频调节： 变频调节主要是通过改变压缩机的转速达到改变工 质的流量和压缩机功耗的目的。 这样在气温不太高的情况下， 可以通过 适当降低压缩机转速而达到节能的目的。
2 ) 膨胀阀调节： 包括热力膨胀阀和电子膨胀阀等。 其调节原理是 通过改变膨胀阀的节流面积达到改变工质流量和膨胀比的目的。
上述两种调节方式均无法改变系统中的工质的平均密度， 或者说工 质的充装量。 理论和实验均证实， 每一工况下都存在一个工质最佳充装 量， 在该最佳充装量下， 系统达到最佳工作状态， 具有最佳能效比。 当 系统偏离了设计工况时，上述两种调节方式均无法改变工质的平均密度， 因此系统就难以处于最佳能效比 （EER或 COP ) 状态下工作。
当机组在空调制冷和热泵工况之间切换时， 上述的问题就特别突 出。 如在夏天制冷工况时， 其外部环境温度区间为 27 °C (室内） 至 35 °C (室外）； 在冬天热泵工况时， 其外部温度区间则为 20 °C (室内）至 2
°C (室外）。 在上述温度条件下， 夏天制冷时， 合理的工质冷凝温度设为 50°C， 蒸发温度为 12°C ; 冬天制热时， 工质的冷凝温度应降为 35°C， 蒸 发温度应降为一 8°C。 显然， 这两个工况下， 工质的工作温度相差了 15 V。 由于在不同的温度下， 气态工质具有不同的密度， 15 °C之差气态工 质的密度差别将达 50%以上。 也就是说， 制冷和热泵工况下， 系统中的 最佳工质充装量将有相当大的差别。 显然， 传统的热泵空调系统难以适 应这种情况， 其工质的充装量若照顾了制冷工况， 则热泵工况工质充装 量将大大过量。 为减小这种差距， 传统的热泵空调系统在设计时有意缩 小室内换热器的面积， 增大室内换热温差。 这样， 夏天制冷时的工质设 计蒸发温度将从 12°C降低至 5V； 而冬天制热时的冷凝温度将从 35°C提 高至 43°C。此时冬、夏两个工况下工质的工作温度的差值将减小到 1CTC 左右， 最佳工质充装量的差别得以缩小，但代价是设计能效比也降低了， 设计能效比将从 4下降到 3左右。
即使在单纯的制冷工况或热泵工况下运行时，传统空调系统的大部 分时间也是偏离设计工况的， 当空调刚启动时， 室内的温度是缓慢下降 的， 而当室内温度稳定后， 室外的温度又可能随时间而变， 传统的空调 的工质充装量无法对此进行精确调节， 这意味着传统的空调系统大多数 时间的工质充装量不处于最佳状态。 发明内容
针对现有技术存在的由于工质的平均密度固定不变，使系统难以 处于最佳能效比 （EER或 COP) 状态下工作的问题， 本发明提出蒸 气压缩式空调系统工质侧容积连续可调的技术方案，使系统中工质平 均密度由固定不变状态变为可调节状态。工质侧容积的变动意味着工 质的平均密度发生了变动， 当循环工质的平均密度增大时， 如果其他 条件不变， 则工质循环的冷凝温度和蒸发温度都升高， 反之亦然。 这 就为空调系统的运行提供了一种新的调节手段，从而有效提高空调系 统的能效比。
本发明所要解决的技术问题是通过如下技术方案实现的： 一种装有能效增大器的蒸气压缩式空调系统，包括压缩机、冷凝 器、 膨胀阀、 蒸发器和依次连接上述各机构的管道组成的工质循环回 路， 在所述的工质循环回路中接入能效增大器， 所述的能效增大器包 括可变容积容器和改变容器容积的执行机构。
进一步地， 系统还包括四通阀， 当在所述的工质循环回路中接入 四通阀时， 切换四通阀可使该循环回路按空调制冷或热泵方式运行。
所述的冷凝器还通过管道与水箱和循环泵连接成水加热循环回 路。
更好地，所述的可变容积容器与工质循环回路的连接位置设置在 压缩机出口的循环管道处。
具体地，所述的可变容积容器为可伸缩变形的波纹管，所述波纹 管的两端分别由底板封闭，所述波纹管的一端底板通过连接管与工质 循环回路管道连接， 所述波纹管的另一端底板与所述的执行机构连 接。 所述的执行机构由螺母丝杠运动副构成， 螺母的外圆为蜗轮， 与 蜗轮相配的蜗杆通过电动机驱动，所述的丝杠的一端与所述波纹管的 底板固定连接。
本发明的装有能效增大器的热泵空调系统可以显著提高系统的 能效比， 使工况能效比可以达到 4左右， 而且其季节能效比还能超过 设计工况能效比， 显著改善空调系统的运行性能。
下面结合附图和具体实施方式对本发明作进一步详细的说明。 附图说明
图 1为实施例 1一单纯空调制冷系统的示意图；
图 2为实施例 2—单纯热泵系统的示意图；
图 3为实施例 3—热泵热水器系统的示意图；
图 4为实施例 4一空调制冷一热泵系统的示意图；
图 5为能效增大器实施例示意图；
图 6为装有能效增大器的系统的循环温熵图。 具体实施方式
图 1为实施例 1一单纯空调制冷系统的示意图， 包括压缩机 1、 冷凝器 （室外机） 3、 膨胀阀 4、 蒸发器 （室内机） 5和依次连接上述 各机构的管道组成的工质循环回路。在所述的工质循环回路中接入能 效增大器 6， 所述的能效增大器由可变容积容器 61 和改变容器容积 的执行机构 62组成。 作为一个最佳实施例， 所述的可变容积容器 61 与工质循环回路的连接位置设置在压缩机 1出口的循环管道处， 因为 该处的循环工质压力高、 密度大， 可变容积容器 61 比较小的容积变 动可对系统循环回路中工质的平均密度产生比较大的影响，调节灵敏 度比较高。当然可变容积容器也可以连接到系统循环回路的其他位置 上， 也可以在循环回路上连接多个可变容积容器。
当夏季室外气温下降时， 工质的冷凝温度也随着下降， 相应的， 工质的冷凝压力和密度也随着下降，循环回路中的工质量处于过量状 态， 这将导致能效比的下降。 此时可稍为扩大可变容积容器 61 的容 积， 减少循环回路中的工质平均密度， 使循环回路中的工质量达到最 佳值， 此时系统具有最佳能效比和制冷能力。 更进一步， 在压缩机转 速不变的条件下， 由于循环回路中的工质平均密度可调， 则经过压缩 机的工质质量流量也可调，从而实现了利用定转速常规压缩机达到变 容量空调的目的。 因此， 本发明具有取代变频空调的潜力。
图 2为实施例 2—单纯热泵系统的示意图， 包括压缩机 1、 冷凝 器 （室内机） 3、 膨胀阀 4、 蒸发器 （室外机） 5和依次连接上述各机 构的管道组成的工质循环回路。在所述的工质循环回路中接入能效增 大器 6， 所述的能效增大器由可变容积容器 61 和改变容器容积的执 行机构 62组成。 作为一个最佳实施例， 所述的可变容积容器 61与工 质循环回路的连接位置设置在压缩机 1出口的循环管道处， 因为该处 的循环工质压力高、 密度大， 可变容积容器 61 比较小的容积变动可 对系统循环回路中工质的平均密度产生比较大的影响，调节灵敏度比 较高。 当然可变容积容器也可以连接到系统循环回路的其他位置上， 也可以在循环回路上连接多个可变容积容器。
当冬季室外气温下降时， 可稍为扩大可变容积容器 61的容积， 降低循环回路中工质的平均密度， 此时工质的蒸发温度也将随着下 降， 使蒸发器保持合理的最佳传热温差， 此时系统在基本不降低能效 比和制热能力的条件下实现低温下的高效制热。
图 3为实施例 3—装有能效增大器的热泵热水器系统示意图，包 括压缩机 1、 冷凝器 3、 膨胀阀 4、 蒸发器 5和依次连接上述各机构 的管道组成的工质循环回路， 其中， 冷凝器 3还和水箱 7及循环泵 8 组成水加热回路。 在所述的工质循环回路中接入能效增大器 6， 所述 的能效增大器由可变容积容器 61 和改变容器容积的执行机构 62组 成。 作为一个最佳实施例， 所述的可变容积容器 61 与工质循环回路 的连接位置设置在压缩机 1出口的循环管道处， 因为该处的循环工质 压力高、 密度大， 可变容积容器 61 比较小的容积变动可对系统循环 回路中工质的平均密度产生比较大的影响， 调节灵敏度比较高。 当然 可变容积容器也可以连接到系统循环回路的其他位置上，也可以在循 环回路上连接多个可变容积容器。
由于热泵热水器的工作特点， 水温是逐渐上升的， 如刚开始加热 时的水温为 10°C， 加热终了的水温升到 55 °C， 因此热泵热水器工质 的冷凝温度也要相应从 25°C增加至 65°C。如果使用环保型工质 134a， 25 °C时气态工质的密度为 32kg/m3， 65 °C时气态工质的密度为 100 kg/m3 , 相差达 3 倍之多。 传统的热泵热水器的工质充装量难以适应 这种情况， 开始加热时处于工质严重过量的状况， 到加热结束时又可 能处于工质量过少的状态。 这都会明显降低热泵热水器的能效比。 使 用本发明， 我们就能妥善的解决这个难题。 在整个加热过程中， 我们 可以使可变容积容器 61 的容积逐渐减少， 也就是使循环回路中工质 的平均密度逐渐增大， 使冷凝器始终处于最佳工作状态， 从而热泵热 水器具有最佳的能效比和最大的工作能力。
图 4为实施例 4一空调制冷一热泵系统的示意图，包括压缩机 1、 四通阀 2、 冷凝器 3、 膨胀阀 4、 蒸发器 5和依次连接上述各机构的 管道组成的工质循环回路，切换四通阀 2可使该循环回路按空调制冷 或热泵方式运行。 在所述的工质循环回路中接入能效增大器 6， 所述 的能效增大器由可变容积容器 61 和改变容器容积的执行机构 62组 成。 作为一个最佳实施例， 所述的可变容积容器 61 与工质循环回路 的连接位置设置在压缩机 1出口的循环管道处， 因为该处的循环工质 压力高、 密度大， 可变容积容器 61 比较小的容积变动可对系统循环 回路中工质的平均密度产生比较大的影响， 调节灵敏度比较高。 当然 可变容积容器也可以连接到系统循环回路的其他位置上，也可以在循 环回路上连接多个可变容积容器。
当本系统工况由空调制冷工况 （如工质冷凝温度为 50°C， 蒸发 温度为 12°C ) 切换为热泵工况 （如工质冷凝温度为 35°C， 蒸发温度 为一 10°C ) 时， 此时可将可变容积容器 61 的容积增大， 以减少循环 回路中的工质平均密度， 从而使工质的冷凝温度由 50°C逐渐降至 35 °C， 相应的工质的蒸发温度由 12°C下降至一 10°C左右， 实现工况的 切换， 使系统能效比保持在 4左右， 比现有空调系统的最佳能效比提 高 10%以上。 反之， 当由制热工况转为制冷工况时， 则可将可变容积 容器 61的容积减少而使工质的充装量适应工质工作温度的变化。
本发明如果和膨胀阀调节或变频调节结合起来就可以实现对空 调一热泵系统的全面精确调节， 从而可以在各种工况下同时使 A Tk 和 A Te调节到最佳值， 此时系统的能效比将达到该工况下的最大值。
图 5 为装有能效增大器的蒸气压缩式空调系统的能效增大器的 实施例示意图。 如图所示， 所述的可变容积容器 61 为可伸缩变形的 波纹管 611， 所述波纹管的两端分别由底板封闭， 所述波纹管的一端 底板 612通过连接管与工质循环管路连接，所述波纹管的另一端底板 613与所述的执行机构 62连接。
所述的执行机构 62由螺母丝杠运动副构成， 螺母 621的外圆为 蜗轮 623， 与蜗轮相配的蜗杆 624通过电动机 625驱动， 所述的丝杠 622的一端与所述波纹管的底板固定连接。 当电动机 625正转或反转 时， 蜗轮螺母 621也跟着正转或反转， 从而使丝杠 622产生前伸或后 缩运动，带动波纹管容器的底板 613运动，达到改变容器容积的目的。
为了减小波纹管容器的死容积， 在所述波纹管的一端底板 613 内侧悍接一段圆柱体 615， 该圆柱体的直径略小于波纹管的内径， 圆 柱体的长度略大于波纹管完全压缩时的长度。
对于压缩机为 2kW 的涡旋式全封闭压缩机， 波纹管的内径为 20cm, 圆柱体 615 的直径为 19.8cm， 当波纹管完全压缩时的长度为
10cm时， 圆柱体的长度为 10.1cm。 圆柱体 614的端面与前底板 613 内侧端面的距离在 0至 15cm之间变动， 对应波纹管的长度在 10cm 至 25cm之间变动。
本发明的能效增大器除了上述实施例的波纹管及其机械驱动机 构以外，还可以有其他结构形式，如活塞式缸体与液压驱动机构配合， 通过液压机构驱动活塞在缸体内的移动来改变缸体内的工质容积。可 变容积容器还可以采用膜盒式、 特殊可变形复合材料式等结构。 图 6为装有能效增大器的空调系统的循环温熵图，其中横坐标 S 代表熵值， 纵坐标 T代表温度值。 改变工质的容积的调节方式的实质 是改变参与循环的工质的平均密度，从而使工质的冷凝温度和蒸发温 度同时升高或降低， 图中用实线表示的封闭曲线 1-2-3-4为设计工况 下的循环曲线， 其中 1-2为工质压缩过程， 2-3为工质冷凝过程， 3-4 为工质膨胀过程， 4-1 为工质蒸发过程。 当减少可变容积容器的容积 时， 参与循环的工质的平均密度增加， 图示的制冷循环曲线 1-2-3-4 整体上移,如曲线 1 ' -2 ' -3 ' -4 ' 所示， 当增大可变容积容器的容积 时， 参与循环的工质的平均密度减少， 图示的制冷循环曲线 1-2-3-4 整体下移， 如曲线 1〃 -2〃 -3〃 -4〃 所示， 此时由于压缩机的转速和 膨胀阀的开度都没变， 因而循环的压缩比没有显著变化。 这是本发明 的调节方式和以往靠改变膨胀比或压缩比的调节方式的根本区别。把 这两种不同的调节方式结合起来可以使空调系统精确满足各种工况 条件下的运行并使系统的能效比始终处于最佳值。

Claims

权利要求书
1、 一种装有能效增大器的蒸气压缩式空调系统， 包括压缩机（1)、 冷凝器（3)、 膨胀阀 （4)、 蒸发器（5)和依次连接上述各机构的管道组 成的工质循环回路， 其特征是， 在所述的工质循环回路中接入能效增大 器 （6)， 所述的能效增大器包括可变容积容器和改变容器容积的执行机 构。
2、根据权利要求 1所述的装有能效增大器的蒸气压缩式空调系统， 其特征是， 还包括四通阀 （2)， 当在所述的工质循环回路中接入四通阀 (2) 时， 切换四通阀可使该循环回路按空调制冷或热泵方式运行。
3、根据权利要求 1所述的装有能效增大器的蒸气压缩式空调系统， 其特征是， 所述的冷凝器还通过管道与水箱 （7) 和循环泵 （8) 连接成 水加热循环回路。
4、 根据权利要求 1至 3任一项所述的装有能效增大器的蒸气压缩 式空调系统， 其特征是， 所述的可变容积容器 （61) 与工质循环回路的 连接位置设置在压缩机 （1) 出口的循环管道处。
5、 根据权利要求 1至 3任一项所述的装有能效增大器的蒸气压缩 式空调系统， 其特征是， 所述的可变容积容器 （61) 为可伸缩变形的波 纹管 （611)， 所述波纹管的两端分别由底板封闭， 所述波纹管的一端底 板（612)通过连接管与工质循环回路管道连接， 所述波纹管的另一端底 板 （613) 与所述的执行机构 （62) 连接。
6、根据权利要求 5所述的装有能效增大器的蒸气压缩式空调系统， 其特征是， 所述的执行机构 （62) 由螺母丝杠运动副构成， 螺母 （621) 的外圆为蜗轮 （623)， 与蜗轮相配的蜗杆 （624) 通过电动机 （625) 驱 动， 所述的丝杠 （622) 的一端与所述波纹管的底板固定连接。
7、根据权利要求 5所述的装有能效增大器的蒸气压缩式空调系统， 其特征是， 在所述波纹管的一端底板（613 )内侧焊接一段圆柱体（614)， 该圆柱体的直径略小于波纹管的内径， 圆柱体的长度略大于波纹管完全 压缩时的长度。
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CN113834247B (zh) * 2015-07-20 2023-09-01 克莱斯泰克雷克Ip私人有限公司 蒸气压缩系统及用于其的子系统

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