CN210512227U - Refrigerant circulation system - Google Patents

Abstract

The utility model discloses a refrigerant circulation system relates to refrigerating system technical field for solve the inconsistent problem of refrigerant physical state in each tonifying qi branch road among the current refrigerant circulation system. The utility model provides a refrigerant circulation system includes main circulation pipeline and tonifying qi pipeline, the main circulation pipeline is including connecting gradually the first heat exchanger on the circulation pipeline between compressor unit's gas vent and compressor unit's air inlet, throttling arrangement, the second heat exchanger, compressor unit includes two at least compressors, the tonifying qi pipeline includes tonifying qi main road and many tonifying qi branch roads, the access connection of tonifying qi main road is between first heat exchanger and throttling arrangement's import, the export of tonifying qi main road respectively with the import intercommunication of many tonifying qi branch roads, the export of tonifying qi branch road and the tonifying qi mouth intercommunication of compressor, in the pipeline of tonifying qi main road, and the refrigerant exit who is located tonifying qi main road is provided with the orifice plate, a plurality of through-holes have been seted up on the orifice plate. The utility model is used for refrigerate or heat.

Description

Refrigerant circulation system

Technical Field

The utility model relates to a refrigerating system technical field that is correlated with especially relates to a refrigerant circulation system.

Background

The refrigeration system is generally a refrigerant circulation system formed by connecting four basic components including a compressor, an evaporator, a condenser and a throttling device through pipelines, and the refrigerant continuously circulates in the refrigerant circulation system, so that a state change occurs and heat exchange is performed with the outside.

In the prior art, a method of providing a gas supplement pipeline is generally adopted to improve the energy efficiency of the refrigerant circulation system. For the scheme that the refrigerant circulation system includes a plurality of compressors, taking the case that the refrigerant circulation system includes two compressors, the refrigerant circulation system also includes two air make-up branches, wherein the two compressors are respectively a first compressor 021 and a second compressor 022, and the two air make-up branches are respectively a first air make-up branch 03 and a second air make-up branch 04, as shown in fig. 1.

In order to improve the energy efficiency of the refrigerant circulating system, when a first air supplement branch 03 connected to an air supplement port of a first compressor 021 and a second air supplement branch 04 connected to an air supplement port of a second compressor 022 are opened, gas-liquid two-phase refrigerant is not uniformly mixed in an air supplement main path 01, so that the states of the refrigerant entering the first air supplement branch 03 and the refrigerant entering the second air supplement branch 04 are inconsistent, and the refrigerant entering the first air supplement branch 03 and the refrigerant entering the second air supplement branch 04 are prone to bias flow, namely, the liquid refrigerant in the refrigerant entering the first air supplement branch 03 is more and the gas refrigerant is less, and the gas refrigerant in the refrigerant entering the second air supplement branch 04 is more and the liquid refrigerant is less; or the liquid refrigerant in the refrigerant entering the first gas supplementing branch 03 is less and the gas refrigerant in the refrigerant entering the second gas supplementing branch 04 is less and the liquid refrigerant is more, so that the first compressor 021 and/or the second compressor 022 are prone to gas supplementing liquid carrying, and when the refrigerant state difference between the refrigerant entering the gas supplementing branch 03 and the refrigerant entering the gas supplementing branch 04 is too large, the gas supplementing superheat degrees of the first compressor 021 and the second compressor 022 are obviously different, and therefore the running stability of the refrigeration cycle system is low.

SUMMERY OF THE UTILITY MODEL

An embodiment of the utility model provides a refrigeration cycle system for the refrigerant attitude of solving among the current refrigeration cycle system each compressor tonifying qi mouth is different, thereby leads to the lower problem of refrigeration cycle system's operating stability.

For reaching above-mentioned purpose, the embodiment of the utility model provides a refrigerant circulation system includes main circulation pipeline and tonifying qi pipeline, the main circulation pipeline is including connecting gradually the first heat exchanger on the circulation pipeline between compressor unit's gas vent and compressor unit's air inlet, throttling arrangement, the second heat exchanger, compressor unit includes two at least compressors, the tonifying qi pipeline includes tonifying qi main road and many tonifying qi branch roads, the access connection of tonifying qi main road is between first heat exchanger and throttling arrangement's import, the export of tonifying qi main road respectively with the import intercommunication of many tonifying qi branch roads, the export of tonifying qi branch road and the tonifying qi mouth one-to-one intercommunication of compressor, the pipeline of tonifying qi main road, and the refrigerant exit who is located tonifying qi main road is provided with the orifice plate, a plurality of through-holes have been seted up on the orifice plate.

Compared with the prior art, the embodiment of the utility model provides an in the pipeline of the main way of tonifying qi among the refrigerant circulating system, and be located the refrigerant exit of the main way of tonifying qi and be provided with the orifice plate, a plurality of through-holes have been seted up on the orifice plate, from this when the two-phase state refrigerant in the refrigerant circulating system flows out through the through-hole on the orifice plate that sets up in the main way of tonifying qi, the flow area of two-phase state refrigerant reduces to the sum of the cross-sectional area of a plurality of through-holes on the orifice plate by the cross-sectional area of the main way of tonifying qi, make partly liquid refrigerant take place the throttle effect when flowing through the through-hole on the orifice plate on the one hand, the throttle is gaseous state refrigerant, but the refrigerant of another part flow through the through-hole still is liquid state refrigerant, the slower liquid state refrigerant of flow velocity drops, thereby preventing the compressor unit from generating the danger of air supply liquid entrainment; on the other hand, the mixing degree of the two-phase refrigerant in the gas supplementing main circuit is enhanced, so that the two-phase refrigerant is uniformly mixed in the physical state, the physical states of the refrigerant entering the plurality of gas supplementing branches tend to be consistent, the phenomenon that the refrigerant is easy to drift is reduced, and the operation stability of the refrigerant circulating system is improved.

Drawings

In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to these drawings without creative efforts.

FIG. 1 is a schematic view showing a structure of a refrigerant cycle system according to the prior art;

fig. 2 is a schematic structural diagram of a refrigerant cycle system according to an embodiment of the present invention;

FIG. 3 is a schematic structural diagram of an air supplement pipeline in an embodiment of the present invention;

FIG. 4 is a schematic view showing a configuration in which a center hole of an orifice plate is a cylindrical through hole in example 1;

FIG. 5 is a side view of the orifice plate of example 1 in which the central hole is a cylindrical through hole;

FIG. 6 is a schematic perspective view showing a flared through-hole as a center hole of the orifice plate in example 2;

FIG. 7 is a schematic view showing a structure in which a center hole of an orifice plate is a trumpet-shaped through hole in example 2;

FIG. 8 is a sectional view of the orifice plate of example 2 in which the center hole is a trumpet-shaped through hole;

FIG. 9 is a schematic perspective view showing a hole of an orifice plate of example 3, the hole having a tapered central hole;

FIG. 10 is a schematic view showing a configuration in which the center hole of the orifice plate is a tapered through-hole in example 3;

FIG. 11 is a cross-sectional view of the central hole of the orifice plate of example 3 being a tapered through hole.

Detailed Description

The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative work belong to the protection scope of the present invention.

In the description of the present invention, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; may be a mechanical connection; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present invention can be understood in specific cases to those skilled in the art.

The terms "central," "upper," "lower," "vertical," "horizontal," "top," "bottom," "inner," "outer," and the like are used in an orientation or positional relationship indicated in the drawings for convenience in describing the invention and to simplify the description, and are not intended to indicate or imply that the device or element so referred to must have a particular orientation, be constructed and operated in a particular orientation, and are therefore not to be construed as limiting the invention.

The terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless otherwise specified.

For a product with a refrigeration cycle system including a compressor unit, a scheme of frequency average distribution needs to be adopted for a plurality of compressors in the compressor unit, that is, in the process of operation of the refrigeration cycle system, the operation frequencies of the plurality of compressors are the same, and then the stable operation of the refrigeration cycle system can be ensured.

Referring to fig. 2-3, the embodiment of the utility model provides a refrigerant circulation system includes main circulation pipeline and tonifying qi pipeline, main circulation pipeline is including connecting gradually first heat exchanger 2 on the circulation pipeline between compressor unit 1's gas vent and compressor unit 1's the air inlet, throttling arrangement 3, second heat exchanger 4, compressor unit 1 includes two at least compressors, tonifying qi pipeline 5 is including tonifying qi main road 51 and many tonifying qi branch roads, the access connection of tonifying qi main road 51 is between first heat exchanger 2 and throttling arrangement 3's import, the export of tonifying qi main road 51 respectively with the import intercommunication of many tonifying qi branch roads, the export of tonifying qi branch road and the tonifying qi mouth one-to-one intercommunication of compressor, in tonifying qi main road 51's the pipeline, and the refrigerant exit that is located tonifying qi main road 51 is provided with orifice plate 6, a plurality of through-holes 7 have been seted up on the orifice plate 6.

Compared with the prior art, the embodiment of the present invention provides a pore plate 6 is disposed in the pipeline of the air supply main path 51 in the refrigerant circulation system and at the refrigerant outlet of the air supply main path 51, a plurality of through holes 7 are disposed on the pore plate 6, therefore, when the two-phase refrigerant in the refrigerant circulation system flows out through the through holes 7 on the pore plate 6 disposed in the air supply main path 51, the flow area of the two-phase refrigerant is reduced from the cross-sectional area of the air supply main path 51 to the sum of the cross-sectional areas of the plurality of through holes 7 on the pore plate, on one hand, a throttling effect occurs when a part of the liquid refrigerant flows through the through holes 7 on the pore plate 6, the throttling is a gaseous refrigerant, but the other part of the refrigerant flowing through the through holes 7 is still a liquid refrigerant, the liquid refrigerant with a slower flowing speed gradually falls back, the fallen refrigerant flows back through the through holes, thereby preventing the compressor unit 1 from generating the danger of air supply liquid entrainment; on the other hand, the mixing degree of the two-phase refrigerant is enhanced, the two-phase refrigerant is uniformly mixed, the refrigerant entering the plurality of air supply branches tends to be consistent in physical state, the phenomenon that the refrigerant is easy to drift is reduced, and the operation stability of the refrigerant circulating system is improved.

It should be noted that: optionally, the number of the compressors in the compressor unit 1 of the refrigerant circulation system is two or more, and the number of the gas supplementing branches of the refrigerant circulation system is two or more. Illustratively, the compressor unit 1 in the above-mentioned refrigerant cycle system includes two compressors, and the plurality of gas supply branches in the above-mentioned refrigerant cycle system are two gas supply branches, where the two compressors are the first compressor 11 and the second compressor 11 respectively, and the two gas supply branches are the first gas supply branch 52 and the second gas supply branch 53 respectively, as shown in fig. 2. The main gas supply path 51, the first gas supply branch 52 and the second gas supply branch 53 are connected through a three-way pipe joint 10, and the orifice plate 6 is arranged in one end of the three-way valve 10 communicated with the main gas supply path 51, as shown in fig. 3.

When the refrigerant circulating system is in a refrigeration or defrosting mode, the compressor unit 1 sucks low-temperature and low-pressure refrigerant gas from the first heat exchanger 2 through the air suction port, the refrigerant gas is compressed into high-temperature and high-pressure refrigerant gas by the compressor unit 1 and then enters the second heat exchanger 4 through the air exhaust port of the compressor unit 1, the high-temperature and high-pressure refrigerant gas releases heat to fluid medium (water or air) in the second heat exchanger 4, the refrigerant gas is condensed into low-temperature and high-pressure liquid, and the low-temperature and low-pressure liquid is throttled by the throttling device 3 and then enters the first heat exchanger 2 to be evaporated and absorbed into low-temperature and low-pressure refrigerant gas and enter the compressor. When the refrigeration cycle system is in a heating mode, the compressor unit 1 sucks low-temperature low-pressure refrigerant gas from the second heat exchanger 4 through the air suction port, the refrigerant gas is compressed into high-temperature high-pressure refrigerant gas by the compressor unit 1 and then enters the first heat exchanger 2 through the air exhaust port of the compressor unit 1, the high-temperature high-pressure refrigerant gas releases heat to fluid medium (water or air) in the first heat exchanger 2, the refrigerant gas is condensed into low-temperature high-pressure liquid, and after the refrigerant gas is throttled into low-temperature low-pressure liquid by the throttling device 3, the refrigerant gas enters the second heat exchanger 4 to absorb heat and evaporate into low-temperature low-pressure refrigerant gas and enters the compressor unit 1.

Optionally, the first branch gas supply 52 and the second branch gas supply 53 are designed identically, that is, the inner diameter of the pipeline, the length of the pipeline, the roughness of the inner surface of the pipeline, and the bending form of the pipeline of the first branch gas supply 52 and the second branch gas supply 53 are identical. For the refrigerant with the state of matter approaching to the same state entering the first air make-up branch 52 and the second air make-up branch 53, the pressure loss of the refrigerant due to the pipeline resistance is also approximately equal, thereby realizing the uniform distribution of the refrigerant entering each compressor air make-up port in the compressor unit 1.

Optionally, the embodiment of the utility model provides an in still include balanced pipeline 54 in the air supplement pipeline, balanced pipeline 54 is used for the tonifying qi pressure between balanced first tonifying qi branch road 52 and the second tonifying qi branch road 53, and balanced pipeline 54's one end and first tonifying qi branch road 52 intercommunication, balanced pipeline 54's the other end and second tonifying qi branch road 53 intercommunication. It is known that liquids or gases flow from a high pressure to a low pressure. When the refrigerant pressures in the first and second make- up branches 52, 53 are not equal, the following two situations occur: one is that the pressure of the refrigerant in the first gas make-up branch 52 is higher than the pressure of the refrigerant in the second gas make-up branch 53, at which time the refrigerant flows into the second gas make-up branch 53 through the balance line 54; the other is that the pressure of the refrigerant in the second air supplement branch 53 is higher than the pressure of the refrigerant in the first air supplement branch 52, and at this time, the refrigerant flows into the first air supplement branch 52 through the balance line 54, so that the pressures of the refrigerants in the first air supplement branch 52 and the second air supplement branch 53 are equal, the air supplement pressures of the air supplement ports of the compressors in the compressor unit 1 are ensured to be equal, and the operation stability of the refrigerant circulating system is improved.

Referring to fig. 3 to 4, the through hole 7 formed in the orifice plate 6 includes a central hole 71 and a flow equalizing hole 72, and the diameter of the central hole 71 is larger than that of the flow equalizing hole 72. When the refrigerant flows through the gas supply main passage 51, a part of the refrigerant flows out through the center hole 71 of the orifice plate 6, and the other part of the refrigerant flows out through the equalizing hole 72 of the orifice plate 6. The diameter of the central hole 71 is larger, so that more refrigerants can enter the first air supplement branch 52 and the second air supplement branch 53, the flow of the refrigerants entering the air supplement ports of the compressors in the compressor unit 1 is larger, and the energy efficiency of a refrigerant circulating system is improved; the diameter of the flow equalizing hole 72 is smaller, the throttling effect of the refrigerant when flowing through the flow equalizing hole 72 is more remarkable, most of liquid refrigerant in the refrigerant flowing through the flow equalizing hole 72 is throttled and gasified into gaseous refrigerant, the risk of liquid entrainment by the compressor unit 1 is reduced, meanwhile, the inner space of the flow equalizing hole 72 is smaller, the mixing degree of the refrigerant is enhanced, and the mixing degree of the refrigerant is higher. Wherein the axis of the central bore 71 coincides with the axis of the orifice plate 6. Optionally, the through hole 7 opened in the orifice plate 6 includes a plurality of equalizing holes 72, and when the orifice plate 6 includes a plurality of equalizing holes 72, the mixing degree of the refrigerant passing through the orifice plate is high.

Based on the above embodiment, although the diameter of the central hole 71 is larger than that of the flow equalizing hole 72, the diameter of the central hole 71 is smaller for the air make-up main passage 51, so that when the refrigerant flows through the central hole 71, a throttling effect also occurs, so that part of liquid refrigerant in the refrigerant flowing through the central hole 71 is throttled and gasified into gaseous refrigerant, and the refrigerant entering the plurality of air make-up branches is guaranteed to have proper dryness, thereby further avoiding the risk of air make-up and liquid entrainment of the compressor unit 1.

Further, referring to fig. 4 to 5, the center hole 71 is a cylindrical through hole. The processing and manufacturing process of the cylindrical through hole is simple and convenient, and the processing cost is low. Optionally, the central hole 71 may be a cylindrical through hole or a square through hole, and compared with the latter, the hole wall of the central hole 71 in the former scheme is smooth and has no edges and corners, so as to reduce the pressure loss when the refrigerant flows through the central hole 71, and therefore the former scheme is preferred in the embodiment of the present invention.

Alternatively, the diameter of the center hole 71 is gradually reduced in the flow direction of the refrigerant, as shown in fig. 6 to 11. After the refrigerant enters the central hole 71, the flow area of the refrigerant is gradually reduced, the volume of the refrigerant is continuously compressed, the throttling effect of the central hole 71 is obvious, more liquid refrigerant in the refrigerant flowing through the central hole 71 is throttled and gasified into gaseous refrigerant, the liquid refrigerant with lower flow speed in the refrigerant flowing out of the central hole 71 starts to fall back under the action of gravity, the fallen refrigerant is gradually accumulated on the surface of the pore plate 6 close to the compressor unit 1 and flows back through the central hole 71 and part of the flow equalizing holes 72, so that the gas-liquid two-phase refrigerant is separated greatly, the dryness of the refrigerant entering an air supplementing port of the compressor unit 1 is improved, the air supplementing liquid entrainment of the compressor unit 1 can be better avoided, and part of the liquid refrigerant is throttled and gasified into the gaseous refrigerant.

Based on the above-mentioned embodiment, the shape of the central hole 71 can be selected from a trumpet-shaped through hole, a taper hole or other shaped holes. Since the special-shaped hole needs to be machined and formed by a special tool, the machining process is complicated, and the manufacturing cost of the orifice plate 6 is also increased, therefore, in the embodiment of the present invention, the shape of the central hole 71 is preferably set to be a trumpet-shaped through hole or a cone-shaped hole.

Further, the utility model discloses centre bore 71 on the orifice plate 6 is tubaeform through-hole, and the tangent line that tubaeform through-hole is close to the pore wall of compressor unit 1's one end is parallel with the axis of orifice plate 6, and the contained angle V between the tangent line that tubaeform through-hole is close to the pore wall of the upper surface of orifice plate 6 and the upper surface of orifice plate 6 in figure 8 is 90 promptly to can guarantee that the refrigerant that flows out through centre bore 71 has better gathering nature, improve the velocity of flow of refrigerant through centre bore 71 with this. The trumpet-shaped through hole is formed by transition from the first end to the second end through the circular arc R, and the hole wall is smooth, so that the pressure loss of the refrigerant flowing through the central hole is reduced. The first end of the horn-shaped through hole is the end, close to the compressor unit 1, of the pore plate 6, and the second end of the horn-shaped through hole is the end, close to the throttling device, of the pore plate 6.

The size of the included angle between the hole wall of the tapered through hole and the lower surface of the hole plate 6 in the above embodiment determines the flow rate of the refrigerant in the plurality of air supply branches, the larger the value of the included angle w, the more the flow rate of the refrigerant in the plurality of air supply branches is, the more the refrigerant enters the air supply ports of the compressors in the compressor unit 1, the smaller the value of the included angle w, the less the flow rate of the refrigerant in the plurality of air supply branches is, and the less the refrigerant enters the air supply ports of the compressors in the compressor unit 1. Optionally, if the central hole 71 is a tapered through hole, the range of the included angle w between the hole wall of the tapered through hole and the plane perpendicular to the axis of the tapered through hole is: 40-60 degrees, namely the value range of the included angle between the hole wall of the conical through hole and the lower surface of the orifice plate 6 in fig. 11 is as follows: 40 deg. -60 deg., as shown in fig. 11. The size of an included angle between the hole wall of the conical through hole and the lower surface of the pore plate 6 determines the flow rate of the refrigerant in the plurality of air supply branches, the larger the value of the included angle w is, the more the flow rate of the refrigerant in the plurality of air supply branches is, the more the refrigerant enters the air supply ports of the compressors in the compressor unit 1, the smaller the value of the included angle w is, the less the flow rate of the refrigerant in the plurality of air supply branches is, and the less the refrigerant enters the air supply ports of the compressors in the compressor unit 1. When the included angle w is larger, more refrigerants enter the air supplement ports of the compressors of the compressor unit 1, the air supplement amount of the compressors is larger, and the operation of a refrigerant circulating system is unstable; when contained angle w is little partially, the refrigerant that gets into the tonifying qi mouth of 1 each compressor of compressor unit is less, is unfavorable for improving refrigerant circulation system's efficiency, from this, the embodiment of the utility model provides an among them the pore wall of toper through-hole and the value scope of contained angle w between the plane of the axis of perpendicular to toper through-hole are preferred: 40 to 60 degrees.

Furthermore, the number of the flow equalizing holes 72 is multiple and is uniformly distributed around the circumference of the central hole 71, the distribution of the refrigerant flowing out of the orifice plate 6 can be relatively uniform through the flow equalizing holes 72 which are uniformly distributed, and the uneven flow of the refrigerant entering the plurality of air supply branches due to the uneven distribution of the flow equalizing holes 72 is prevented, so that the inconsistent flow of the refrigerant entering the air supply ports of the compressors in the compressor unit 1 in the refrigerant circulating system is avoided, and the operation stability of the refrigerant circulating system is improved.

Alternatively, the above-mentioned flow equalizing holes 72 are uniformly distributed around the circumference of the central hole 71, and the flow equalizing holes 72 may be arranged in one turn around the circumference of the central hole 71, as shown in fig. 4; the flow equalizing holes 72 may be arranged in a plurality of circles around the circumference of the central hole 71, for example, the flow equalizing holes 72 may be arranged in three circles around the circumference of the central hole 71, and the flow equalizing holes 72 arranged in a plurality of circles are arranged in the radial direction of the central hole 71 in an aligned manner, as shown in fig. 6 to 7, the number of the flow equalizing holes 72 in the present invention is not particularly limited, when the present invention is used in a specific manner, the number of the flow equalizing holes 72 may be determined according to the refrigerant state in the gas supplementing main 51, the flow rate of the refrigerant, the strength of the orifice plate 6, and other parameters, and the flow equalizing holes 72 arranged in a plurality of circles may not be aligned in the radial direction of the central hole 71, as long as the flow equalizing holes 72 are ensured to be uniformly and symmetrically distributed around the circumference.

It should be noted that: if diameter d of flow equalizing hole 72₆Less than 3mm, the flow resistance of the refrigerant passing through the equalizing hole 72 is large, resulting in a large pressure loss of the refrigerant passing through the equalizing hole 72, and the air pressure of the refrigerant passing through the equalizing hole 72 is large, resulting in a large noise generated when the refrigerant passes through the equalizing hole 72; if diameter d of flow equalizing hole 72₆Greater than 5mm, the flow area when refrigerant flows through the flow equalizing hole 72 is great to weaken the throttle effect of the flow equalizing hole 72 to the refrigerant, from this, the embodiment of the utility model provides an in diameter d of flow equalizing hole 72₆The value range of (A) is preferably as follows: 3-5 mm.

The thickness H of the pore plate 6 is less than 3mm, so that the manufacturing difficulty of the pore plate 6 is increased, the pore plate 6 is easy to deform under the impact of refrigerant, and the safety is low; in addition, in order to reduce the manufacturing cost of the orifice plate 6 and reduce the resistance loss when the refrigerant flows through the through hole 7 on the orifice plate 6, it is more to guarantee the refrigerant that gets into the air supplement port of each compressor in the compressor unit 1, thereby further improving the energy efficiency of the refrigerant cycle system, and the thickness H of the orifice plate 6 can not be greater than 5mm, therefore, the embodiment of the utility model provides a thickness H of the orifice plate 6 must satisfy the following relation: h is more than or equal to 3mm and less than or equal to 5 mm.

In order to ensure that the orifice plate 6 is simply, conveniently, stably and reliably mounted, the orifice plate 6 in the refrigerant circulating system is in interference fit with the pipeline of the gas supplementing main passage 51. For example, the orifice plate 6 and the main air supply passage 51 are both of an annular structure, and if the fit between the orifice plate 6 and the pipelines of the main air supply passage 51 is clearance fit, the connection force between the orifice plate 6 and the pipelines of the main air supply passage 51 is weak, and under the pressure of refrigerant, the orifice plate 6 slides easily in the pipelines of the main air supply passage 51 and even falls off from the pipelines of the main air supply passage 51, so that the orifice plate 6 cannot perform the function of flow equalization.

The material cost of copper or copper alloy is low, so that the manufacturing cost of the orifice plate 6 can be reduced; the copper or copper alloy has better heat-conducting property and is easy to process. Therefore, the material of the orifice plate in the embodiment of the present invention is preferably copper or copper alloy. In addition, the orifice plate 6 may be made of other materials with lower cost and better heat conductivity, such as aluminum or aluminum alloy.

Further, the refrigerant circulating system further comprises an economizer 8, the economizer 8 comprises a first heat exchange flow path and a second heat exchange flow path which exchange heat with each other, the first heat exchange flow path is connected between an inlet of the air supply main path 51 and the throttling device 3, the second heat exchange flow path is connected in series with the air supply main path 51, when the refrigerant enters the second heat exchange flow path in the economizer 8, the heat of the refrigerant in the first heat exchange flow path in the economizer 8 can be absorbed, so that the temperature of the refrigerant at an outlet of the second heat exchange flow path in the economizer 5 is increased, the refrigerant in the air supply main path 51 has proper air supply superheat degree, the danger of air supply liquid carrying of the compressor unit 1 is further avoided, and the operation stability of the compressor unit 1 is improved.

Optionally, the refrigerant cycle system further comprises a flow control valve 9, and the flow control valve 9 is disposed on a communication pipeline between an inlet of the make-up gas main 51 and an inlet of the second heat exchange flow path in the economizer 8. Because the refrigerant flow in the second heat exchange flow path in the economizer 8 determines the heat transfer quantity between the first heat exchange flow path and the second heat exchange flow path in the economizer 8, when the opening degree of the flow control valve 9 in the refrigerant circulation system is adjusted, the heat absorbed by the refrigerant in the second heat exchange flow path in the economizer 8 is correspondingly changed, so that the air supplement superheat degree of the compressor unit 1 is changed, the air supplement superheat degree of the compressor unit 1 is prevented from being too high or too low, and the problem that the energy efficiency of the refrigerant circulation system is low due to the fact that the exhaust temperature of the compressor unit 1 is too high or too low is solved.

According to the data that system performance and noise test under the different operating modes of refrigerant cycle system obtained, can set up above-mentioned centre bore 71 into different structural parameters to satisfy the demand under the different operating modes, it is right to combine three specific orifice plate embodiment below the utility model discloses in the embodiment of the utility model the structural parameter of centre bore 71 among the orifice plate 6 carries out further explanation.

Example 1

The working condition that the air supplementing temperature is higher, the mixing degree of the gas-liquid two-phase refrigerant is not high and the separation is easy is met. Referring to FIGS. 4-5, orifice plate 6 and air make-up assemblyThe paths 51 are all annular, and the diameter of the pore plate 6 is d₁The central hole 71 is a cylindrical through hole, and the diameter of the central hole 71 has a value range of: (1/4) < d >₁～(1/2)*d₁. If the diameter of central bore 71 is less than (1/4) × d₁At this time, the size of the central hole 71 is smaller, and the flow resistance of the refrigerant flowing through the central hole 71 is increased, so that the pressure loss of the refrigerant is larger, the pressure of the refrigerant entering the air supplement port of the compressor 1 is reduced, and the energy efficiency of the refrigerant circulating system is not favorably improved; if the diameter of central bore 71 is greater than (1/2) × d₁At this time, the size of the central hole 71 is too large, which may cause the strength of the orifice plate 6 to be reduced, and the gas-liquid two-phase refrigerant may not be sufficiently mixed when passing through the central hole 71, which may decrease the mixing degree of the refrigerant.

Example 2

The working conditions that the air supplementing temperature is low, the mixing degree of the gas-liquid two-phase refrigerant is high or the liquid refrigerant in the refrigerant is more are met. Similarly, referring to fig. 8, the orifice plate 6 and the air supply main passage 51 are both annular structures, and the diameter of the orifice plate 6 is d₁The center hole 71 is a trumpet-shaped through hole, and the diameter d of one end of the center hole 71 near the upper surface of the orifice plate 6₂The value range is as follows: (1/16) < d >₁～(1/8)*d₁And the diameter d of the end of the central hole 71 near the lower surface of the orifice plate 6₃The value range is as follows: (3/8) < d >₁～(1/8)*d₁The pressure loss of the refrigerant when flowing through the trumpet-shaped through hole can be made lower, and the mixing degree of the refrigerant is more appropriate.

Example 3

The amount of air supplement required for the compressor unit 1 is large, and the liquid refrigerant in the refrigerant is less. Similarly, referring to fig. 11, the orifice plate 6 and the air supply main passage 51 are both annular structures, and the diameter of the orifice plate 6 is d₁The center hole 71 is a tapered through hole, and the diameter d of the end of the center hole 71 near the upper surface of the orifice plate 6₄The value range is as follows: (1/8) < d >₁～(3/8)*d₁And the diameter d of the end of the central hole 71 near the lower surface of the orifice plate 6₅The value range is as follows: d₄+2 × tanw, the pressure loss of the refrigerant when flowing through the trumpet-shaped through hole can be made low,and the mixing degree of the refrigerants is proper.

In the description herein, particular features, structures, materials, or characteristics may be combined in any suitable manner in any one or more embodiments or examples.

The above description is only for the specific embodiments of the present invention, but the protection scope of the present invention is not limited thereto, and any changes or substitutions that can be easily conceived by those skilled in the art within the technical scope of the present invention should be covered by the protection scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims.

Claims (10)

1. A refrigerant circulating system is characterized by comprising a main circulating pipeline and an air supplementing pipeline, the main circulation pipeline comprises a first heat exchanger, a throttling device and a second heat exchanger which are sequentially connected on the circulation pipeline between an exhaust port of the compressor unit and an air inlet of the compressor unit, the compressor unit comprises at least two compressors, the air supply pipeline comprises an air supply main pipeline and a plurality of air supply branch pipelines, the inlet of the air supply main path is connected between the first heat exchanger and the inlet of the throttling device, the outlet of the air supply main path is respectively communicated with the inlets of the plurality of air supply branches, the outlets of the air supply branches are correspondingly communicated with the air supply ports of the compressor one by one, and a pore plate is arranged in the pipeline of the gas supplementing main path and positioned at the refrigerant outlet of the gas supplementing main path, and a plurality of through holes are formed in the pore plate.

2. The refrigerant cycle system of claim 1, wherein the makeup line further comprises a balancing line for balancing a makeup pressure of the refrigerant in the plurality of makeup branches.

3. The refrigerant cycle system as set forth in claim 1, wherein said through hole includes a center hole and a plurality of equalizing holes, a diameter of said center hole being larger than a diameter of said equalizing holes.

4. The refrigerant cycle system of claim 3, wherein the central bore is a cylindrical through bore.

5. The refrigerant cycle system as set forth in claim 3, wherein said central hole is gradually reduced in diameter in a flow direction of the refrigerant.

6. The refrigerant cycle system of claim 5, wherein the central hole is a flared through hole or a tapered through hole.

7. The refrigerant cycle system as set forth in claim 6, wherein a tangent of a hole wall of said trumpet-shaped through hole at an end close to said compressor block is parallel to an axis of said orifice plate.

8. The refrigerant cycle system of claim 6, wherein the angle between the hole wall of the tapered through hole and a plane perpendicular to the axis of the tapered through hole has a value in the range of: 40 to 60 degrees.

9. A refrigerant cycle system as set forth in any one of claims 3 to 8, wherein a plurality of said flow equalizing holes are uniformly distributed around a circumference of said center hole.

10. The refrigerant cycle system as set forth in claim 1, wherein the thickness H of said orifice plate satisfies the following relationship: h is more than or equal to 3mm and less than or equal to 5 mm.

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