High-energy-efficiency vortex structure

Abstract

The utility model discloses a vortex structure with high energy efficiency, which relates to the field of elastic fluid pumps, and comprises a static vortex and a dynamic vortex, the static vortex and the dynamic vortex form a compression chamber, one side of a static vortex disc part of the static vortex is provided with static vortex teeth, the other side of the static vortex is provided with a high-low pressure annular partition plate, and the static vortex disc part of the static vortex is provided with a high-low pressure annular partition plate. And the static scroll plate part is provided with a central exhaust port, a plurality of medium-pressure exhaust ports and a plurality of enhanced vapor injection ports which are respectively and correspondingly provided with valve plates for matching. According to the scroll compressor, the efficiency of the compressor can be effectively improved no matter under the low-pressure-ratio operation working condition or the high-pressure-ratio operation working condition, energy efficiency reduction caused by over-compression and under-compression of the scroll compressor is reduced, and the efficient operation range of the scroll compressor is widened.

Description

TECHNICAL FIELD

[0001] The utility model relates to the field of elastic fluid pump, concretely relates to a high energy efficiency scroll structure of arc engagement. BACKGROUND

[0002] The design of scroll compressor has been produced in the early twentieth century, but is limited to the precision and surface roughness of mechanical processing at that time, and has not been widely used instead of piston compressor, and with the progress of mechanical processing level, the advantages of scroll compressor also gradually begin to appear.

[0003] The scroll compressor is smooth in operation, small in vibration, quiet in working environment, and is also known as'super-quiet compressor'. The scroll compressor is novel and precise in structure, has the advantages of small size, low noise, light weight, small vibration, small energy consumption, long service life, continuous and stable gas transmission, reliable operation, clean gas source and the like. It is known as 'new revolutionary compressor' and 'no maintenance compressor', and is an ideal power source for pneumatic machinery, and is widely used in industries, agriculture, transportation, medical devices, food decoration, textile and other industries and other occasions requiring compressed air.

[0004] However, the existing scroll compressor cannot balance the internal and external pressures of the compression chamber, when the outdoor environment temperature is relatively low, the working pressure of the refrigeration system is relatively low, due to the constant pressure ratio characteristic of the scroll compressor, at this time, the compression of the scroll on the gas belongs to over-compression, that is, the gas pressure in the compression chamber is compressed to be higher than the exhaust back pressure before the compression chamber is communicated with the exhaust port, such as the 'electric vehicle scroll compressor moving disc and head pressure relief groove design method' disclosed in the announcement number CN118564454A, which lacks a solution to the over-compression condition. UTILITY MODEL CONTENTS

[0005] The utility model aims at providing a scroll structure capable of early exhaust at low pressure ratio operation and jet energy increase at high pressure ratio operation.

[0006] The present application achieves the above technical purpose by the following technical means.

[0007] A high energy efficiency scroll structure, comprising a static scroll and a dynamic scroll, the static scroll and the dynamic scroll form a compression chamber, one side of the static scroll disc part of the static scroll is provided with a static scroll tooth, the other side of the static scroll is provided with a high-low pressure annular partition, the static scroll disc part is provided with a center exhaust port, a plurality of medium pressure exhaust ports and a plurality of jet energy increase ports and is respectively provided with a valve piece.

[0008] Further, one side of the orbiting scroll is provided with orbiting scroll teeth, and the center position of the fixed scroll plate is provided with a center exhaust port which does not interfere with the orbiting scroll teeth and the fixed scroll teeth.

[0009] As preferred, the number of the medium pressure exhaust ports is two, which are a first medium pressure exhaust port and a second medium pressure exhaust port, and are symmetrically distributed on the two sides of the center exhaust port.

[0010] The number of the jet augmentor ports is two, which are a first jet augmentor port and a second jet augmentor port, and are symmetrically distributed on the two sides of the center exhaust port and are located outside the medium pressure exhaust ports.

[0011] Further, the first jet augmentor port and the second jet augmentor port are not located on the same straight line with the first medium pressure exhaust port and the second medium pressure exhaust port, and do not overlap with the fixed scroll teeth.

[0012] Further, a horizontal hole position plane is symmetrically provided on the edge of the fixed scroll plate in a direction with a certain angle with the center exhaust port and the medium pressure exhaust port, and the height of the horizontal hole position plane is lower than the height of the root of the fixed scroll teeth.

[0013] Further, a first jet augmentor horizontal hole and a second jet augmentor horizontal hole are transversely provided above the horizontal hole position plane in the fixed scroll plate, and the jet augmentor horizontal hole is perpendicular to and communicates with the jet augmentor port.

[0014] Further, a screw mounting hole is provided in the high-low pressure annular partition plate, the screw mounting hole is cooperatively mounted with the exhaust valve plate and the stopper, and the stopper covers the exhaust valve plate.

[0015] Further, an angle exists between the stopper and the exhaust valve plate, the exhaust valve plate is divided into a plurality of valve plates, each valve plate is further provided on one opening of the fixed scroll plate, and each valve plate is independently controlled to be opened or closed.

[0016] Further, the orbiting scroll comprises an orbiting scroll plate and orbiting scroll teeth, the phase difference between the fixed scroll teeth and the orbiting scroll teeth is 180°, the axis of the orbiting scroll is radially offset from the axis of the fixed scroll by a distance of one revolution radius, and a plurality of pairs of crescent-shaped compression chambers are formed.

[0017] As preferred, an O-shaped groove is provided on the outside of the high-low pressure annular partition plate, and a sealing element is provided in the O-shaped groove.

[0018] The utility model has the following beneficial effects:

[0019] Compared with the prior art, the scroll compressor structure can effectively improve the efficiency of the compressor under the operation condition of low pressure ratio or high pressure ratio, reduces the energy efficiency reduction caused by over-compression and under-compression of the scroll compressor, and widens the range of efficient operation of the scroll compressor. BRIEF DESCRIPTION OF DRAWINGS

[0020] Figure 1 It is a structure schematic view of the scroll tooth of the static scroll of the utility model.

[0021] Figure 2 It is a structure schematic view of the high-low pressure annular partition plate of the static scroll of the utility model.

[0022] Figure 3 It is a structure schematic view of the scroll tooth of the dynamic scroll of the utility model.

[0023] Figure 4 It is a structure schematic view of the other side of the dynamic scroll.

[0024] Figure 5 It is a side view sectional view of the transverse hole of the static scroll of the utility model.

[0025] Figure 6 It is a side view sectional view of the medium pressure exhaust port of the static scroll of the utility model.

[0026] Figure 7 It is a structure schematic view of the stopper of the utility model.

[0027] Figure 8 It is a structure schematic view of the exhaust valve plate of the utility model.

[0028] Figure 9 It is a dynamic static scroll assembly structure schematic view of the dynamic scroll angle of the utility model.

[0029] Figure 10 It is an assembly structure schematic view of the static scroll, the stopper and the exhaust valve plate of the utility model.

[0030] Figure 11 It is a cooperation structure schematic view of the static scroll tooth and the dynamic scroll tooth of the utility model.

[0031] Figure 12 It is a sectional structure schematic view of the compressor of the utility model.

[0032] Figure 13 It is a structure schematic view of the compressor of the utility model.

[0033] In the figure, 1 is a stationary vortex; 1-1 is a stationary vortex disk; 1-2 is a lower plane of a protrusion; 1-3 is a cross-shaped slip ring groove of a stationary vortex; 1-4 is a bolt hole of a protrusion; 1-5 is a stationary vortex tooth; 1-6 is an upper plane of a protrusion; 1-7 is a plane at a transverse hole; 1-8 is a high-low pressure annular partition; 1-9 is an O-groove; 1-10 is a central exhaust port; 1-11 is a first steam injection enthalpy-increasing port; 1-12 is a second steam injection enthalpy-increasing port; 1-13 is a first medium-pressure exhaust port; 1-14 is a second medium-pressure exhaust port; 1-15 is a screw mounting hole; 1-16 is a first steam injection enthalpy-increasing transverse hole; and 1-17 is a second steam injection enthalpy-increasing port. Horizontal hole 1-17; Moving scroll 2; Moving scroll tooth 2-1; Moving scroll disk 2-2; Moving scroll cross ring groove 2-3; Bearing mounting seat 2-4; Arched groove 2-5; Limiter 3; First limit plate 3-1; Second limit plate 3-2; Third limit plate 3-3; Fourth limit plate 3-4; Fifth limit plate 3-5; Limiter mounting hole 3-6; Exhaust valve plate 4; First valve plate 4-1, Second valve plate 4-2, Third valve plate 4-3, Fourth valve plate 4-4, Fifth valve plate 4-5; Valve plate mounting hole 4-6; Connector 7; Check valve 8. Detailed Implementation

[0034] The technical solution of the invention will be further described in detail below through specific embodiments and in conjunction with the accompanying drawings.

[0035] Example 1:

[0036] like Figures 1 to 13 As shown, a high-efficiency vortex structure is characterized by comprising a stationary vortex 1 and a moving vortex 2, wherein the stationary vortex 1 and the moving vortex 2 form a compression chamber, wherein one side of the stationary vortex disk 1-1 of the stationary vortex 1 is provided with stationary vortex teeth 1-5, and the other side of the stationary vortex is provided with high and low pressure annular baffles 1-8, wherein the stationary vortex disk 1-1 is provided with a central exhaust port 1-10 and several medium-pressure exhaust ports and several jet enthalpy-increasing ports, and each is respectively provided with corresponding valve plates.

[0037] The moving vortex 2 consists of a moving vortex tooth 2-1 and a moving vortex disk 2-2. The tooth profile of the moving vortex tooth 2-1 can be generated according to design requirements using various curve functions, including circular involute, algebraic spiral or Archimedean spiral. It is calculated using the meshing principle to form a planar closed compression area that ensures sealing. Finally, the tooth profile is generated by methods such as vertical stretching.

[0038] The moving scroll tooth 2-1 is mounted and fixed on the moving scroll disk part 2-2. To prevent unnecessary rotation of the moving scroll 2 during compressor operation, a moving scroll cross-slip ring groove 2-3 is provided on the moving scroll disk part 2-2 for mating with the cross-slip ring assembly and constraining the movement trajectory of the moving scroll. A bearing mounting seat 2-4 is provided at the center of the back of the moving scroll disk part 2-2 for mounting a bearing and supporting the eccentric rotational motion of the moving scroll.

[0039] To optimize the symmetry of the compressor discharge process and reduce the discharge pulsation caused by the asymmetric structure of the compression chamber, thereby reducing the vibration and noise level during the operation of the compressor, the center end position of the orbiting scroll tooth 2-1 is specially designed with an arc-shaped groove 2-5.

[0040] When the orbiting scroll 2 rotates to the preset discharge angle, the arc-shaped groove 2-5 at the center position of the orbiting scroll cooperates with the groove structure corresponding to the center position of the fixed scroll 1 to form an arc-shaped communication port. The communication port functions to connect the center compression chamber with the secondary center compression chambers symmetrically distributed around the periphery, i.e., the crescent-shaped compression chambers, thereby improving the symmetry of the overall discharge process and helping to improve the smoothness of the operation of the compressor.

[0041] The fixed scroll 1 is composed of a fixed scroll plate part 1-1 and a fixed scroll tooth 1-5 located on the surface of the fixed scroll plate part 1-1. To facilitate the axial installation and positioning of the fixed scroll 1 in the compressor, at least three lower planes 1-2 of the protrusions with consistent heights are provided on the fixed scroll plate part 1-1 along the extension direction of the fixed scroll tooth 1-5, and these planes constitute the reference surface for the installation of the fixed scroll. On the lower planes 1-2 of the protrusions, protrusion bolt holes 1-4 are provided for the installation of bolts to fix the fixed scroll 1 with the shell of the compressor.

[0042] To limit the rotation of the orbiting scroll 2 in the working state, a fixed scroll cross slip ring groove 1-3 is provided on the assembly contact surface between the fixed scroll plate part 1-1 and the orbiting scroll 2. The slip groove forms a perpendicular intersection with the orbiting scroll cross slip ring groove 2-3 to jointly constrain the movement of the orbiting scroll.

[0043] On the side of the fixed scroll plate part 1-1 where the scroll tooth is attached, at least one steam injection enthalpy-increasing port is reasonably provided according to the working pressure ratio range of the compressor. In the embodiment of the present application, the number of steam injection enthalpy-increasing ports is set to two, i.e., a first steam injection enthalpy-increasing port 1-11 and a second steam injection enthalpy-increasing port 1-12, to adapt to the wider operating condition requirements.

[0044] In addition, the fixed scroll 1 is also provided with a first medium-pressure discharge port 1-13 and a second medium-pressure discharge port 1-14 to realize the function of multi-stage discharge or intermediate pressure output. The center discharge port 1-10 is positioned in the central region of the fixed scroll plate part 1-1 and is close to the tooth head part of the fixed scroll tooth 1-5. Such a layout is conducive to optimizing the discharge path of high-pressure gas. The shape profile of the center discharge port 1-10 corresponds to the tooth head modification profile of the fixed scroll tooth 1-5.

[0045] On the back of the static scroll 1, a raised upper plane 1-6 is formed in a position corresponding to a raised lower plane 1-2 used for positioning the static scroll 1, and is also used for mounting and fixing bolts, cooperating with the lower plane to form a stable connection structure of the static scroll 1.

[0046] The high-low pressure annular partition plate 1-8 is designed with the center of the static scroll plate 1-1 as the center, in a ring structure, completely covering the first and second steam injection enthalpy-increasing openings 1-11 and 1-12, ensuring effective separation of the high and low pressure areas.

[0047] In order to realize the function of steam injection enthalpy-increasing, first and second steam injection enthalpy-increasing horizontal holes 1-16 and 1-17 are respectively provided on the side of the static scroll plate 1-1, which are respectively connected to the internal passages of the first and second steam injection enthalpy-increasing openings 1-11 and 1-12 on the static scroll plate. On the static scroll plate 1-1, a horizontal hole plane 1-7 is formed in a position corresponding to the external interfaces of the first and second steam injection enthalpy-increasing horizontal holes 1-16 and 1-17, facilitating reliable connection of external pipelines with the steam injection enthalpy-increasing horizontal holes.

[0048] The high-low pressure annular partition plate 1-8 of the static scroll 1 encloses an exhaust cavity, in which an exhaust valve plate 4 and a stopper 3 are installed, forming a composite exhaust control mechanism. The exhaust valve plate 4 adopts a five-valve plate structure, including valve plate one 4-1, valve plate two 4-2, valve plate three 4-3, valve plate four 4-4, and valve plate five 4-5, which are respectively accurately corresponding to the positions of the first and second steam injection enthalpy-increasing openings 1-11 and 1-12, the first and second medium pressure exhaust openings 1-13 and 1-14, and the central exhaust opening 1-10 on the static scroll plate, realizing independent control of different exhaust ports. The exhaust valve plate 4 is provided with a valve plate mounting hole 4-6, which cooperates with a screw mounting hole 1-15 to mount the exhaust valve plate 4 on the static scroll 1.

[0049] In order to limit the maximum opening degree of the exhaust valve plate 4, a stopper 3 is also installed in the exhaust cavity. The stopper 3 is provided with multiple stop plates, each corresponding to a valve plate on the exhaust valve plate 4, and a predetermined stop gap is reserved between the stop plates and the valve plates.

[0050] In this embodiment, the position limiter 3 is also equipped with five position limiting plates, namely the first position limiting plate 3-1, the second position limiting plate 3-2, the third position limiting plate 3-3, the fourth position limiting plate 3-4 and the fifth position limiting plate 3-5, which correspond to the five valve plates of the exhaust valve plate 4 one by one, to ensure effective limitation of the opening of each valve plate. The main function of the position limiter 3 is to prevent the valve plate from opening excessively during operation, to protect the valve plate from over-stress damage, and to ensure that the valve plate can be quickly closed when it needs to be closed, so that the closing speed is not delayed due to the excessive opening of the valve plate. The position limiter 3 is provided with a position limiter mounting hole 3-6, and the position limiter 3 is mounted above the exhaust valve plate 4. The position limiter mounting hole 3-6 is matched and mounted with the screw mounting hole 1-15 of the static scroll 1, so that the position limiter 3 is also mounted with the static scroll.

[0051] The static scroll 1 mainly includes a static scroll disc part 1-1 and a static scroll tooth 1-5, and the dynamic scroll 2 mainly includes a dynamic scroll disc part 2-2 and a dynamic scroll tooth 2-1. In the actual assembly process, the static scroll tooth 1-5 and the dynamic scroll tooth 2-1 maintain a phase deviation of 180°, which is a basic condition for the scroll compressor to achieve effective compression. The axis of the dynamic scroll 2 is offset from the axis of the static scroll 1 by a rotation radius in the radial direction. This eccentric design enables the dynamic scroll tooth 2-1 of the dynamic scroll 2 and the static scroll tooth 1-5 of the static scroll 1 to maintain engagement, forming multiple pairs of crescent-shaped working chambers therebetween, which are the places where gas compression is achieved.

[0052] In order to control the circumferential position of the dynamic scroll 2 relative to the static scroll 1 and ensure that the dynamic scroll can only perform the expected revolution motion, avoiding the occurrence of rotation phenomenon, a cross slide ring mechanism is adopted for motion constraint. The exhaust valve plate 4 and the position limiter 3 are mounted on the back of the static scroll disc part 1-1, and the specific installation area is the annular space surrounded by the high-low pressure annular partition plate 1-8.

[0053] The five valve plates on the exhaust valve plate 4, namely valve plate one 4-1, valve plate two 4-2, valve plate three 4-3, valve plate four 4-4 and valve plate five 4-5, correspond to the five exhaust ports opened on the static scroll 1, including the first steam injection enthalpy increasing port 1-11, the second steam injection enthalpy increasing port 1-12, the first medium pressure exhaust port 1-13, the second medium pressure exhaust port 1-14 and the center exhaust port 1-10, to realize the sealing and opening / closing control of the exhaust port.

[0054] The exhaust valve plate 4 and the position limiter 3 are reliably fixed in the screw mounting hole 1-15 in the annular area defined by the high-low pressure annular partition plate 1-8 on the back of the static scroll disc 1-1 through screw fastening, ensuring the structural stability of the exhaust mechanism. The center exhaust port 1-10 is located in the central area of the static scroll disc part 1-1 and is adjacent to the tooth head root of the static scroll tooth 1-5.

[0055] In order to further improve the compression performance, the tooth head part of the dynamic scroll tooth 2-1 and the static scroll tooth 1-5 is usually profiled with a double circular arc plus a straight line to reduce gas leakage and improve the volumetric efficiency of the compressor. The shape design of the center exhaust port 1-10 is also consistent with the tooth head correction shape, which ensures smooth discharge of the gas flow and reduces the flow resistance.

[0056] The scroll assembly is usually installed on the upper part of the compressor housing. The static scroll 1 is integrated with a high-low pressure annular partition plate 1-8, and the annular area surrounded by the partition plate forms an independent exhaust chamber inside the compressor for collecting and guiding the compressed high-pressure gas out of the compressor.

[0057] The outer surface of the high-low pressure annular partition plate 1-8 is processed with an annular O-shaped groove 1-9, and an O-shaped sealing ring is embedded in the annular O-shaped groove 1-9. The O-shaped ring on the outer side of the high-low pressure annular partition plate 1-8 on the back of the static scroll 1 bottom plate 1-1 plays a sealing isolation role inside the compressor housing, effectively separating the high-pressure area and the low-pressure area inside the compressor, preventing unnecessary leakage of high and low pressure gases, and helping to improve the compression efficiency and the reliability of the system operation.

[0058] The first steam injection enthalpy increasing horizontal hole 1-16 and the second steam injection enthalpy increasing horizontal hole 1-17 of the static scroll 1 are reliably externally connected to the joint 7 at the position of the horizontal hole of the plane 1-7 through an external pipeline, and a one-way valve 8 is installed in series on the external pipeline of the joint 7. The one-way valve 8 ensures that the refrigerant working medium can only flow into the scroll compressor in one direction, prevents high-pressure gas from flowing back to the low-pressure side of the steam injection enthalpy increasing pipeline, and ensures the normal operation of the system.

[0059] The static scroll 1 is integrated with two steam injection enthalpy increasing ports, two medium pressure exhaust ports, and a center exhaust port 1-10, which are all in communication with the internal space of the compression chamber to realize the functions of multi-stage exhaust and steam injection enthalpy increasing. The flow areas of the steam injection enthalpy increasing ports and the medium pressure exhaust ports are all smaller than that of the center exhaust port 1-10 in structural design, which is designed to realize staged exhaust, optimize the compression process, and improve the compression efficiency.

[0060] Specifically, the two steam injection enthalpy increasing ports are a first steam injection enthalpy increasing port 1-11 and a second steam injection enthalpy increasing port 1-12, which are mainly used to introduce low-pressure refrigerant steam from the economizer; the two medium pressure exhaust ports are a first medium pressure exhaust port 1-13 and a second medium pressure exhaust port 1-14, which are used to discharge part of the medium pressure gas during the compression process to reduce the compression ratio of the subsequent high-pressure stage and reduce the compression power consumption.

[0061] The first medium-pressure exhaust port 1-13 is arranged between the central exhaust port 1-10 and the first steam injection enthalpy-increasing port 1-11 in position, and the second medium-pressure exhaust port 1-14 is arranged between the central exhaust port 1-10 and the second steam injection enthalpy-increasing port 1-12, and the purpose of this port layout is to optimize the flow path of gas at different pressure levels and improve system performance.

[0062] The static scroll 1 is also designed with two steam injection enthalpy-increasing horizontal holes that are connected with the internal passages of the compression chamber, and the horizontal holes are connected with the economizer through external return pipelines, and the return pipelines are also provided with one-way valves 8 to prevent the backflow of refrigerant.

[0063] The steam injection enthalpy-increasing horizontal holes are arranged horizontally on the static scroll plate 1-1, and the two horizontal holes are connected with the internal passages of the corresponding steam injection enthalpy-increasing ports, so as to ensure that the refrigerant steam provided by the economizer can smoothly enter the intermediate compression stage of the scroll compressor and participate in the subsequent compression process.

[0064] The high-temperature and high-pressure liquid refrigerant from the condenser is distributed to two main flow paths after entering the economizer, forming two mutually coordinated refrigeration cycle loops. The first loop is the steam injection enthalpy-increasing loop, and the liquid refrigerant in the economizer undergoes throttling and heat absorption vaporization processes, and is converted into low-temperature and low-pressure refrigerant gas. Subsequently, the low-temperature gas is injected into the intermediate compression chamber of the scroll compressor through the steam injection enthalpy-increasing horizontal hole structure reserved on the static scroll plate 1-1, and is mixed with the refrigerant steam being compressed, to participate in the subsequent compression process, realize quasi-secondary compression, and improve the overall compression efficiency.

[0065] The second loop is the main refrigerant loop, and the liquid refrigerant in the main loop is cooled by the low-temperature refrigerant steam generated by the steam injection enthalpy-increasing loop in the economizer, and the temperature is further reduced, and the supercooling degree of the liquid is increased. Since the supercooling degree of the liquid refrigerant entering the evaporator is increased, the initial enthalpy is reduced, so that more heat can be absorbed during the evaporation and heat absorption process in the evaporator, thereby effectively improving the refrigerating capacity of the evaporator and improving the refrigeration performance of the system.

[0066] The working process of the compressor under different operating conditions has certain self-adaptive adjustment capability, and the specific operation logic is as follows:

[0067] In a low pressure ratio operating environment, for example, when the outdoor ambient temperature is low, the refrigeration system operates under a low exhaust suction pressure ratio condition: in this operating condition, the scroll compressor works in a state of gas over-compression, that is, the actual compression end pressure is higher than the required exhaust pressure of the system. When the gas pressure inside the compression chamber reaches and exceeds the preset exhaust back pressure value during the compression process, the compressor will start the staged exhaust strategy, preferentially discharging part of the high-pressure gas through the first and second jet enthalpy ports 1-11 and 1-12, or further through the first and second medium-pressure exhaust ports 1-13 and 1-14 when the pressure is higher, to adapt to the operating requirements of low pressure ratio and reduce the energy loss caused by over-compression.

[0068] More specifically, in the case of extremely low system pressure ratio, the compressor mainly discharges gas through the first and second jet enthalpy ports 1-11 and 1-12; when the system pressure ratio rises to a certain extent, the first and second jet enthalpy ports 1-11 and 1-12 are closed by the exhaust valve plate 4, at this time, the gas in the compression chamber will be mainly discharged from the first and second medium-pressure exhaust ports 1-13 and 1-14 and the center exhaust port 1-10; finally, the remaining high-pressure gas is discharged from the center exhaust port 1-10 of the compressor, through this multi-stage split exhaust control, effectively avoiding the over-compression energy loss phenomenon that is prone to occur in traditional scroll compressors under low pressure ratio operating conditions, and improving the operating efficiency under low pressure ratio operating conditions. In the process of over-compression exhaust, the center exhaust port 1-10 is always exhausting.

[0069] In a high pressure ratio operating environment, for example, when the outdoor ambient temperature is high, the refrigeration system operates under a high exhaust suction pressure ratio condition: in a high pressure ratio operating condition, the scroll compressor works in a state of gas under-compression, that is, the actual compression end pressure is lower than the required exhaust pressure of the system. When the scroll compression chamber is about to communicate with the center exhaust port 1-10 during the rotation process, the exhaust valve plate 4 will act in coordination to temporarily block the first and second jet enthalpy ports 1-11 and 1-12, the first and second medium-pressure exhaust ports 1-13 and 1-14, and the center exhaust port 1-10, preventing the gas in the compression chamber from being discharged prematurely.

[0070] The refrigerant vapor in the compression chamber will be continuously compressed until the gas pressure is sufficiently raised and significantly higher than the back pressure value of the exhaust line, then the valve plate of the center exhaust port 1-10 will be opened to start the final exhaust process. This exhaust control strategy effectively makes up for the under-compression loss that is prone to occur in traditional scroll compressors under high pressure ratio operating conditions, and reduces the additional energy consumption caused by repeated compression.

[0071] In addition, under the operating condition of high system pressure ratio, the refrigerant usually generates large irreversible loss in throttling process, reducing the overall energy efficiency of the system. In order to recover as much energy loss as possible caused by the irreversible process, the utility model introduces an economizer cycle, which divides a part of liquid refrigerant to the economizer, throttles and depressurizes and partially evaporates in the economizer, so as to reach the intermediate pressure state.

[0072] The low-temperature refrigerant vapor generated by evaporation is accurately injected into the intermediate compression chamber of the scroll compressor through the steam injection enthalpy increasing joint 7 and the preset first steam injection enthalpy increasing horizontal hole 1-16 and the second steam injection enthalpy increasing horizontal hole 1-17, realizes the jet enthalpy increasing refrigeration cycle mode, and improves the system energy efficiency. The low-temperature refrigerant vapor generated by evaporation in the economizer provides the pre-cooling condition for the liquid refrigerant in the main refrigerant circuit while entering the compressor, significantly reduces the temperature of the liquid refrigerant in the main circuit, and increases the supercooling degree.

[0073] Finally, the liquid refrigerant entering the evaporator has higher enthalpy value, so that more heat can be absorbed in the evaporation process, the purpose of improving the evaporator refrigerating capacity is achieved, and the coefficient of performance (COP) of the whole refrigeration system is improved, realizing higher system energy efficiency level.

Claims

1. A high-efficiency vortex structure, characterized in that, It includes a static vortex (1) and a dynamic vortex (2), the static vortex (1) and the dynamic vortex (2) form a compression chamber. The static vortex (1) has a static vortex tooth (1-5) on one side of the static vortex disk (1-1) and a high and low pressure annular baffle (1-8) on the other side. The static vortex disk (1-1) is provided with a central exhaust port (1-10), a number of medium pressure exhaust ports and a number of jet enthalpy-increasing ports, and valve plates are respectively provided for cooperation.

2. The high-efficiency vortex structure according to claim 1, characterized in that, The moving vortex (2) has a moving vortex tooth (2-1) on one side, and a central exhaust port (1-10) is provided at the center of the stationary vortex disk (1-1). The central exhaust port (1-10) does not interfere with the stationary vortex tooth (1-5) and the moving vortex tooth (2-1).

3. The high-efficiency vortex structure according to claim 1, characterized in that, There are two medium-pressure exhaust ports, namely the first medium-pressure exhaust port (1-13) and the second medium-pressure exhaust port (1-14), which are symmetrically distributed on both sides of the central exhaust port (1-10); There are two jet enthalpy-enhancing ports, namely the first jet enthalpy-enhancing port (1-11) and the second jet enthalpy-enhancing port (1-12), which are symmetrically distributed on both sides of the central exhaust port (1-10) and located outside the medium-pressure exhaust port.

4. The high-efficiency vortex structure according to claim 3, characterized in that, The first jet enthalpy-increasing port (1-11) and the second jet enthalpy-increasing port (1-12) are not located on the same straight line as the first medium-pressure exhaust port (1-13) and the second medium-pressure exhaust port (1-14), and do not overlap with the static vortex tooth (1-5).

5. A high-efficiency vortex structure according to claim 1, 3, or 4, characterized in that, In a direction that forms a certain angle with the line connecting the central exhaust port (1-10) and the medium-pressure exhaust port, a horizontal hole plane (1-7) is symmetrically provided on the edge of the static vortex disk (1-1), and the height of the horizontal hole plane (1-7) is lower than the height of the root of the static vortex tooth (1-5).

6. The high-efficiency vortex structure according to claim 5, characterized in that, Above the plane (1-7) at the transverse hole, a first jet enthalpy-increasing transverse hole (1-16) and a second jet enthalpy-increasing transverse hole (1-17) are provided transversely in the static vortex disk part (1-1). The jet enthalpy-increasing transverse holes are perpendicular to and connected to the jet enthalpy-increasing port.

7. A high-efficiency vortex structure according to claim 1, 2, 3, 4, or 6, characterized in that, The high and low pressure annular partition (1-8) is provided with screw mounting holes (15), which are installed in conjunction with the exhaust valve plate (4) and the limiter (3), and the limiter (3) covers the exhaust valve plate (4).

8. A high-efficiency vortex structure according to claim 7, characterized in that, There is an angle between the limiter (3) and the exhaust valve plate (4). The exhaust valve plate (4) is provided with several valve plates. Each valve plate is also on an opening of the static vortex disk (1-1). Each valve plate is individually controlled to open and close.

9. A high-efficiency vortex structure according to claim 1, 2, 3, 4, 6, or 8, characterized in that, The moving vortex (2) includes a moving vortex disk (2-2) and a moving vortex tooth (2-1). The static vortex tooth (1-5) and the moving vortex tooth (2-1) are 180° out of phase. The axis of the moving vortex (2) is radially offset by a rotation radius along the axis of the static vortex (1), forming several pairs of crescent-shaped compression chambers.

10. A high-efficiency vortex structure according to claim 1, 2, 3, 4, 6, or 8, characterized in that, The outer side of the high and low pressure annular partition (1-8) is provided with an O-groove (1-9), and a sealing element is provided in the O-groove (1-9).

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