CN112576503B

CN112576503B - Compressor and air conditioning system

Info

Publication number: CN112576503B
Application number: CN202011396200.5A
Authority: CN
Inventors: 胡余生; 魏会军; 张洪玮; 韩鑫; 彭慧明; 任丽萍
Original assignee: Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
Current assignee: Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
Priority date: 2020-12-03
Filing date: 2020-12-03
Publication date: 2022-12-09
Anticipated expiration: 2040-12-03
Also published as: CN112576503A

Abstract

The invention provides a compressor and an air conditioning system, wherein the compressor comprises a shell, an enthalpy increasing component and a plurality of compression parts arranged in the shell, each compression part comprises a cylinder, a piston and a sliding sheet which are arranged in the cylinder, the plurality of compression parts comprise a low-pressure compression part and a high-pressure compression part, the cylinder in the low-pressure compression part is provided with a low-pressure working cavity, the cylinder in the high-pressure compression part is provided with a high-pressure working cavity, a medium-pressure cavity is arranged in the shell, the enthalpy increasing component is communicated with the medium-pressure cavity, and the sliding sheet in at least one compression part is hinged to the corresponding piston. By adopting the scheme, the sliding sheet is hinged with the piston, so that the sliding sheet and the piston are prevented from being separated while the compression requirement is met, the reliability is improved, and in addition, through the enthalpy-increasing component and the middle pressure cavity, a gaseous refrigerant can be supplemented into the compressor, and the performance of the compressor is improved. The improved compressor not only increases the use effect, but also meets the requirements of the compressor on operation stability, low noise, high efficiency and the like after exceeding the operation range of the compressor.

Description

Compressor and air conditioning system

Technical Field

The invention relates to the technical field of compressors, in particular to a compressor and an air conditioning system.

Background

Along with the continuous widening of the application range of the rotor type compressor, the operation frequency range is wider and wider, the working conditions are more and more complicated and changeable, and the problems of insufficient cold quantity, hydraulic oil operation, high-frequency high-pressure-difference reliability abrasion and the like are easy to occur under extreme working conditions; the main reason is that the sliding vane is easy to disengage due to the following problem under the condition of low operating frequency or existence of compressed liquid in the traditional rotor compressor, thereby causing leakage and abnormal sound; under the working conditions of high frequency and high pressure difference, the sliding sheet is loaded, so that the abrasion problem is easy to occur.

Meanwhile, with the increase of the use scenes of the compressor, many unconventional operation conditions also require that the compressor has enough operation capacity to meet the performance of the air conditioning system during operation under extreme conditions, so that the improvement of phenomena such as liquid compression and the like only from the pump body of the compressor is not enough to meet the use requirements of the system.

Disclosure of Invention

The invention provides a compressor and an air conditioning system, which are used for improving the reliability and performance of the compressor.

In order to achieve the above object, according to one aspect of the present invention, there is provided a compressor including a casing, an enthalpy increasing member, and a plurality of compression portions disposed in the casing, each of the compression portions including a cylinder, and a piston and a vane disposed in the cylinder, the plurality of compression portions including a low pressure compression portion and a high pressure compression portion, the cylinder in the low pressure compression portion having a low pressure working chamber, the cylinder in the high pressure compression portion having a high pressure working chamber, and the casing having an intermediate pressure chamber therein, wherein the enthalpy increasing member and the intermediate pressure chamber are communicated, and at least one vane in the compression portion is hinged to the corresponding piston.

Further, the volume ratio of the high-pressure working chamber to the low-pressure working chamber is 0.5-1.2, and the volume ratio of the medium-pressure working chamber to the low-pressure working chamber is greater than 2.

Further, the sliding sheet in each compression part is hinged with the corresponding piston; wherein, the piston has the holding tank, the one end of gleitbretter with the articulated cooperation of holding tank, the other end of gleitbretter is located in the spout of cylinder.

Further, the compression part further comprises a bearing matched with the end face of the cylinder, and the bearing is provided with an exhaust port; the exhaust port intersects an inner circle of the cylinder in a projection of a radial cross section of the cylinder.

Furthermore, the cylinder has the induction port, have the tangent plane on the outer wall of piston, the tangent plane, the gleitbretter with the region between the inner wall of cylinder constitutes the intercommunication the area of breathing in of induction port.

Further, the cavity in the shell is cylindrical, each compression part is provided with an air outlet, and the numerical value of the sum of the areas of the air outlets of the multiple compression parts is larger than the inner diameter of the shell.

Further, the cavity in the casing is cylindrical, and the length of the casing is more than or equal to two times of the inner diameter of the casing.

The compressor further comprises a crankshaft, the pistons of the compression parts are sleeved on the crankshaft, the distance between the axis of the crankshaft and the axis of the pistons is an eccentric amount A, the crankshaft comprises a long shaft and a short shaft, the diameter of the long shaft is 2A-3A, and the diameter of the short shaft is 2A-2.5A.

Further, the ratio of the height of the cylinder to the inner circle diameter of the cylinder is greater than or equal to 0.5.

Further, the compression part comprises an upper end cover and a lower end cover, the cylinder is positioned between the upper end cover and the lower end cover, the contact area between the upper end surface of the piston and the upper end cover is B, the contact area between the lower end surface of the piston and the lower end cover is C, and B and C are not equal; and/or the contact area of the upper end surface of the slip sheet and the upper end cover is D, the contact area of the lower end surface of the slip sheet and the lower end cover is E, and D is not equal to E.

Further, at least one of the sliding pieces in the plurality of compression parts comprises a first plate body and a second plate body which are connected with each other, wherein the end part of the first plate body is matched with the piston, and the second plate body is matched with the sliding groove of the cylinder; in the axial direction of the cylinder, the size of the second plate body is smaller than that of the first plate body.

Further, the middle pressure chamber is located in a region between the plurality of compression parts and the inner wall of the housing, the air outlet of the low pressure compression part is communicated with the middle pressure chamber, and the air inlet of the high pressure compression part is communicated with the middle pressure chamber.

Further, the compressor further comprises a motor and an oil return pipe, the motor is in driving connection with the plurality of compression parts, an exhaust cavity is formed between the upper portion of the motor and the inner wall of the shell, an oil pool is formed between the lower portions of the plurality of compression parts and the inner wall of the shell, the oil pool is spaced from the medium-pressure cavity, an exhaust port of the high-pressure compression part is communicated with the exhaust cavity, and the exhaust cavity is communicated with the oil pool through the oil return pipe.

According to another aspect of the present invention, there is provided an air conditioning system including the compressor described above.

The invention provides a compressor, which comprises a shell, an enthalpy increasing component and a plurality of compression parts arranged in the shell, wherein each compression part comprises a cylinder, a piston and a sliding sheet which are arranged in the cylinder, the plurality of compression parts comprise a low-pressure compression part and a high-pressure compression part, the cylinder in the low-pressure compression part is provided with a low-pressure working cavity, the cylinder in the high-pressure compression part is provided with a high-pressure working cavity, the shell is internally provided with a medium-pressure cavity, the enthalpy increasing component is communicated with the medium-pressure cavity, and the sliding sheet in at least one compression part is hinged with the corresponding piston. By adopting the scheme, the sliding sheet is hinged with the piston, so that the sliding sheet and the piston are prevented from being separated while the compression requirement is met, the reliability is improved, and in addition, through the enthalpy-increasing component and the middle pressure cavity, a gaseous refrigerant can be supplemented into the compressor, and the performance of the compressor is improved.

Drawings

The accompanying drawings, which are incorporated in and constitute a part of this application, illustrate embodiments of the invention and, together with the description, serve to explain the invention and not to limit the invention. In the drawings:

fig. 1 is a schematic structural diagram of a compressor according to a first embodiment of the present invention;

fig. 2 shows a schematic view of the structure of the compressing part of fig. 1;

FIG. 3 shows a partial enlarged view of FIG. 2;

FIG. 4 shows an assembly schematic of the crankshaft, piston, and slide of FIG. 1;

FIG. 5 illustrates an assembly view of a crankshaft, a piston, and a vane in a compressor according to a second embodiment of the present invention;

FIG. 6 is a schematic view illustrating an assembly of a crankshaft, a piston and a vane in a compressor according to a third embodiment of the present invention;

fig. 7 is a schematic structural view illustrating a compressor according to a fourth embodiment of the present invention;

fig. 8 shows a schematic structural diagram of an air conditioning system according to a fifth embodiment of the present invention.

Wherein the figures include the following reference numerals:

10. a housing; 11. a medium pressure chamber; 12. an exhaust chamber; 13. an oil sump; 20. an enthalpy increasing component; 30. a compression section; 31. a cylinder; 32. a piston; 321. cutting into noodles; 33. sliding blades; 331. a first plate body; 332. a second plate body; 34. a suction area; 40. a crankshaft; 50. a motor; 60. a liquid separator; 71. an indoor heat exchanger; 72. an outdoor heat exchanger; 73. a four-way valve; 74. a flash evaporator.

Detailed Description

The technical solution in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention. It is to be understood that the described embodiments are merely exemplary of the invention, and not restrictive of the full scope of the invention. The following description of at least one exemplary embodiment is merely illustrative in nature and is in no way intended to limit the invention, its application, or uses. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.

As shown in fig. 1 to 4, an embodiment of the present invention provides a compressor, including a shell 10, an enthalpy-increasing component 20, and a plurality of compression portions 30 disposed in the shell 10, each compression portion 30 including a cylinder 31, and a piston 32 and a sliding vane 33 disposed in the cylinder 31, the plurality of compression portions 30 including a low-pressure compression portion and a high-pressure compression portion, the cylinder 31 in the low-pressure compression portion having a low-pressure working chamber, the cylinder 31 in the high-pressure compression portion having a high-pressure working chamber, and the shell 10 having a medium-pressure chamber 11, wherein the enthalpy-increasing component 20 is communicated with the medium-pressure chamber 11, and the sliding vane 33 in at least one compression portion 30 is hinged to the corresponding piston 32. Wherein the plurality is at least two. Optionally, the compressor further comprises a liquid separator 60, the liquid separator 60 being in communication with the inlet of the low pressure compression part. The low-pressure working chamber, the medium-pressure chamber 11 and the high-pressure working chamber are communicated in sequence to realize the flowing and compression of the refrigerant.

By adopting the scheme, the sliding sheet 33 is hinged with the piston 32, so that the sliding sheet 33 is prevented from being separated from the piston 32 while the compression requirement is met, the reliability is improved, and in addition, through the enthalpy-increasing component 20 and the middle-pressure cavity 11, a gaseous refrigerant can be supplemented into the compressor, so that the performance of the compressor is improved.

In the present embodiment, the volume ratio of the high-pressure working chamber to the low-pressure working chamber is 0.5 to 1.2, and the volume ratio of the medium-pressure chamber 11 to the low-pressure working chamber is greater than 2. When the compressor is in operation, the sliding sheet embedded in the piston reciprocates in the sliding sheet groove of the cylinder, and the piston swings. The piston and the sliding sheet are all embedded to form a moving mechanism, the movement of the moving mechanism is not different from that of a conventional structure, but the sliding sheet does not have the risk of separation under the embedding action of the sliding sheet and the piston, and the tail part of the moving mechanism does not need a spring to provide force for pressing the outer circular surface of the piston, so the operation stability of the moving mechanism is ensured by the rigidity of materials at the embedding part of the sliding sheet and the piston, and the moving mechanism has quality change compared with a mode that a spring with a conventional structure generates flexible variable force to ensure the long-term movement stability, and not only is the moving stability of the moving mechanism, but also the tail part gas force is the key for balancing the moving system. The above parameter ranges improve the performance of the compressor under different conditions.

Specifically, the sliding vane 33 in each compression portion 30 is hinged to the corresponding piston 32; wherein, piston 32 has the holding tank, and the one end and the holding tank of gleitbretter 33 are articulated to be cooperated, and the other end of gleitbretter 33 is located the spout of cylinder 31. Therefore, in the running process, the sliding piece 33 is always connected with the piston 32, and the sliding piece 33 is prevented from being separated. In this embodiment the receiving slot has a circular arc wall and the end of the slide 33 is shaped to match the circular arc wall.

In the present embodiment, the compression part 30 further includes a bearing fitted to an end surface of the cylinder 31, the bearing having an exhaust port; the exhaust port intersects the inner circle of the cylinder 31 on a projection of a radial cross section of the cylinder 31. Here, a bearing is also understood to mean a cover plate or a flange. Alternatively, in the case where the piston 32 is operated to the exhaust end position, the area of the exhaust port is larger than the area of the area surrounded by the side of the vane 33, the side of the piston 32, and the inner circumferential surface of the cylinder 31.

In this embodiment, the cylinder 31 has an air inlet, the outer wall of the piston 32 has a cut 321, and the area between the cut 321, the sliding vane 33 and the inner wall of the cylinder 31 constitutes an air inlet area 34 communicating with the air inlet. With the above arrangement, it is possible to ensure that gas is sucked into the suction chamber of the cylinder 31 from the outside of the cylinder 31.

In the present embodiment, the chamber in the housing 10 has a cylindrical shape, each compression part 30 has an exhaust port, and the sum of the areas of the exhaust ports of the plurality of compression parts 30 is greater than the inner diameter of the housing 10. The significance lies in that: when the compressor discharge capacity increases, can realize not changing on original series, satisfy the design of the big discharge capacity of small-size model, can reduce compressor cost.

In the present embodiment, the cavity inside the housing 10 is cylindrical, and the length of the housing 10 is greater than or equal to twice the inner diameter of the housing 10. Due to the large discharge capacity setting, the compressor needs a larger internal space to process the noise generated by the operation of the compressor, so the height of the compressor needs to be adjusted to reserve a larger upper and lower cavity space of the motor to eliminate the noise; when the volume of a working cavity of a compressor is changed without changing a series, the shell of the compressor needs to be lifted to adapt to the increase of the flow of time domain refrigerant caused by the increase of the volume of the working cavity of the compressor, and meanwhile, the oil return treatment needs to be carried out on lubricating oil mixed in discharged refrigerant by using larger upper and lower cavity spaces of a motor due to the increase of the flow of the refrigerant, so that the height of the shell is two times larger than the inner diameter of the shell.

In the present embodiment, the compressor further includes a crankshaft 40, the pistons 32 of the plurality of compression parts 30 are all sleeved on the crankshaft 40, a distance between an axis of the crankshaft 40 and an axis of the piston 32 is an eccentric amount a, the crankshaft 40 includes a major axis and a minor axis, a diameter of the major axis is 2A-3A, and a diameter of the minor axis is 2A-2.5A. The compressor needs to reduce the friction power consumption of the compressor in the design of large displacement, and the excessive power consumption of the compressor brings great test to the abrasion of a moving part and the service life of a motor, so that the shaft diameter of a crankshaft of the compressor needs to be shortened in the design process, and the eccentricity can be correspondingly increased to improve the volume of an actual working cavity of the compressor.

Alternatively, δ is a ratio of the thickness of the piston 32 to the inner diameter of the housing 10, and a height difference between the cylinder 31 and the piston 32 is equal to or greater than 3 δ and equal to or less than 4 δ. The piston 32 may also be referred to as a roller. When the compressor is designed in a certain extreme range, the sealing distance between the piston and the end cover plate in the axial direction is easy to guarantee, so that the radial leakage amount of the piston is controlled by narrowing the distance between the piston and the end cover plate in the radial direction, and the reduction of the leakage amount is crucial to the operation efficiency of the pump body; it is set in the above range because it needs to be adjusted according to the inner diameter of the housing.

In the present embodiment, the ratio of the height of the cylinder 31 to the inner circle diameter of the cylinder 31 is 0.5 or more. The air-supplying enthalpy-increasing compressor with the sliding-vane embedded structure is required to be applied to various new refrigerant systems, part of refrigerants are very sensitive to the radial friction area and the axial heat transfer coefficient of the compressor, the structure of the compressor is required to be further widened according to the characteristics of the new refrigerants, and the design that the energy efficiency ratio of the new refrigerant sliding-vane embedded air-supplying enthalpy-increasing compressor is better than or equal to 0.5 can be ensured when the energy efficiency ratio is set to be more than or equal to 0.5.

In this embodiment, the compressing portion 30 includes an upper end cover and a lower end cover, and the cylinder 31 is located between the upper end cover and the lower end cover, where a contact area between the upper end surface of the piston 32 and the upper end cover is B, a contact area between the lower end surface of the piston 32 and the lower end cover is C, and B and C are not equal; and/or the contact area of the upper end face of the sliding sheet 33 and the upper end cover is D, the contact area of the lower end face of the sliding sheet 33 and the lower end cover is E, and D and E are not equal.

Aiming at a two-stage enthalpy-increasing compressor pump body structure applying a sliding vane embedded structure, upper and lower chamfers of a piston are different, and the two-stage enthalpy-increasing compressor pump body structure is characterized in that the sealing area of an upper end face and an upper end cover of the piston is larger than that of a lower end face and a lower end cover of the piston. In the conventional structure, the thicknesses of upper and lower oil films of a piston under the action of gravity are different, the distances between the upper and lower oil films and upper and lower end covers are also different, the upper chamfer and the lower chamfer of the piston are different, the oil pressure action of the piston floats when the piston runs, the acting force is opposite to the gravity of the piston, the upper end surface and the upper end cover keep the upper oil film seal and simultaneously lift the piston, the distance between the lower end surface and the lower end cover of the piston is increased, and the thickness of the lower oil film is increased; the thickness of the upper oil film is reduced to facilitate sealing, the thickness of the lower oil film is increased to facilitate boundary lubrication, leakage is reduced by reducing the thickness of the upper oil film, the thickness of the lower oil film is increased to reach the thickness of the boundary lubricating oil film, the relative motion damping coefficient is greatly reduced, the contact area is reduced, and the motion friction loss of the lower end surface is reduced. When the operation state in the pump body is stable, the expansion coefficient of the piston is stable, the thicknesses of the upper oil film and the lower oil film reach a critical lubrication state, the sealing and friction loss of the upper end surface and the lower end surface are kept to be reduced, and the operation efficiency of the pump body is improved remarkably.

In the present embodiment, the middle pressure chamber 11 is located in a region between the plurality of compression parts 30 and the inner wall of the casing 10, the outlet port of the low pressure compression part communicates with the middle pressure chamber 11, and the inlet port of the high pressure compression part communicates with the middle pressure chamber 11.

The low-pressure stage compression cavity sucks refrigerant from the large liquid separator, the refrigerant is directly discharged from the medium-pressure cavity in the shell and is mixed with saturated refrigerant introduced from the enthalpy increasing component of the flash evaporator, the high-pressure stage compression cavity directly sucks the mixed refrigerant from the medium-pressure cavity in the shell for compression, and the discharged refrigerant is directly discharged through a connecting pipe between the silencer and the exhaust pipe. The structure utilizes the inside of the shell as a medium-pressure cavity, and the ratio of the actual working volume of the medium-pressure cavity relative to the double-stage air-supplying enthalpy-increasing compression cavity is enlarged by a plurality of times, so that the air-supplying efficiency of the structure is far superior to that of the middle cavity formed by a conventional flange, the pump body can realize the design of single-stage double air discharge or larger displacement which is difficult to realize in the conventional double-stage enthalpy-increasing structure, and the performance improvement space performance of the structure is excellent. Simultaneously, the medium-pressure cavity can effectively utilize the heat generated by compression and a motor, the mixing efficiency of the medium-pressure cavity is improved, the air supplement amount which is several times that of a conventional structure can be realized in the ultra-low temperature or the working condition with large residual supercooling degree, the refrigerating capacity for lifting the low-pressure level on the system is greatly facilitated, meanwhile, the pulsation phenomenon generated when two kinds of source gas in the medium-pressure cavity are mixed can be well eliminated, the high-pressure level air suction loss is reduced, and the compression power is improved. Finally, due to the use of the sensitivity of the sliding vane embedded structure to the sliding vane backpressure, when the pressure cavity is used as the sliding vane back pressure, the force applied to two side walls by crossing in the sliding vane groove when the sliding vane is embedded with the piston and moves can be reduced, the friction power consumption of the side surface of the sliding vane is reduced, the vibration of the embedded moving part when the backpressure is too large is reduced, the integrity of the noise enhancement embedded part on the operation time domain is reduced, and a large space is designed for large-displacement design and high-speed design of the compressor.

As shown in fig. 7, in the fourth embodiment, different from the above embodiments, the compressor further includes a motor 50 and an oil return pipe, the motor 50 is in driving connection with the plurality of compressing units 30, a discharge chamber 12 is provided between the upper side of the motor 50 and the inner wall of the casing 10, an oil sump 13 is provided between the lower part of the plurality of compressing units 30 and the inner wall of the casing 10, the oil sump 13 is spaced from the middle pressure chamber 11, the discharge port of the high pressure compressing unit is communicated with the discharge chamber 12, and the discharge chamber 12 is communicated with the oil sump 13 through the oil return pipe. The oil sump 13 and the intermediate pressure chamber 11 being spaced apart is also understood to mean that the oil sump 13 and the intermediate pressure chamber 11 are not in communication.

The upper part and the lower part are both designed to return oil, so that a better oil return space of the compressor at a high exhaust temperature can be ensured, and the oil return space is a high-pressure cavity separated from the medium-pressure cavity. Due to the different temperatures of the medium and high pressure chambers, the oil settings of the two parts are different, which results in: in the medium-pressure cavity, more liquid refrigerants carried in refrigerants introduced from a large liquid separator (namely, behind the second-stage throttle valve) are still provided with the liquid refrigerants probably when the refrigerants are discharged after being compressed by the low-pressure stage, the liquid refrigerants cannot be directly dissolved in the refrigeration oil due to contact with the high-temperature oil pool, the refrigeration oil with higher temperature cannot be reduced in viscosity coefficient due to heat exchange of the liquid refrigerants with lower temperature, and the friction loss of a pump body is increased; in the high-pressure cavity, oil contained in the refrigerant discharged after being compressed by the high-pressure stage flows back to the bottom oil pool in the upper high-pressure cavity, enters the pump body from the short shaft of the crankshaft, participates in the lubrication of the pump body, and has little lubricating oil discharged in the medium-pressure cavity along with the pump body, so that a moving part of the pump body is lubricated; oil in the two pressure chambers are separated from each other, the oil content in exhaust gas is less, the oil amount required to be filled by the compressor is reduced by more than 30% compared with that of a conventional two-stage compressor, and the compressor has excellent performance on the design space of the compressor, the performance improvement amount of the compressor and the long-term motion life.

The compressor combining the characteristics can be designed to greatly increase the discharge capacity of the original system, and can also be designed at high speed due to the integrity of the moving part, and can be applied to more fields because the problem of the clicking sound influencing the refrigerating capacity and the heating effect is solved, for example, an R290 clothes dryer system with higher requirements on the safety of refrigerants and electric appliances, a CO2 system with higher requirements on pressure difference and the like can be adopted. In conclusion, the two-stage air-supply enthalpy-increasing compressor can greatly widen the application field and various indexes of the compressor by combining the sliding-vane embedded technology, and greatly improves the compatibility and development potential of the new design of the compressor.

Alternatively, there is an exhaust passage in the motor 50, and the exhaust port of the high-pressure compression part is communicated with an exhaust chamber through the exhaust passage, and the flow area of the exhaust chamber is larger than the volume of the high-pressure working chamber.

As shown in fig. 5 and 6, in the second and third embodiments, unlike the first embodiment, at least one sliding piece 33 of the plurality of compression parts 30 includes a first plate 331 and a second plate 332 connected to each other, wherein an end of the first plate 331 is engaged with the piston 32, and the second plate 332 is engaged with the sliding groove of the cylinder 31; the second plate body 332 is smaller in size than the first plate body 331 in the axial direction of the cylinder 31. This facilitates the achievement of unequal contact areas between the two end faces of the piston and the two end caps.

When the piston and the slip sheet are in embedded operation, the stable operation state of the piston can drive the slip sheet in nested connection, the thickness of the oil film in the axial direction can be reduced, the thickness of the oil film in the axial direction can be increased, the slip sheet is set to be in a mode with different upper and lower end surfaces, the stable operation state is also the stable operation state of the piston, the free swing motion piece can meet the critical lubrication state in the axial direction, the mechanical loss in operation is stably reduced, and the theoretical isentropic compression power is improved.

As shown in fig. 8, embodiment 5 of the present invention provides an air conditioning system including the above-described compressor.

Specifically, the air conditioning system comprises an indoor heat exchanger 71, an outdoor heat exchanger 72, a four-way valve 73 and a flash evaporator 74, wherein the outdoor heat exchanger 72 is connected with the four-way valve 73, the indoor heat exchanger 71 is connected with the four-way valve 73, an air outlet of a shell 10 of the compressor is connected with the four-way valve 73, a liquid separator 60 of the compressor is connected with the four-way valve 73, the outdoor heat exchanger 72 is connected with the flash evaporator 74, one branch of the flash evaporator 74 is connected with the enthalpy increasing component 20, and the other branch of the flash evaporator 74 is connected with the indoor heat exchanger 71. The refrigerant discharged by the compressor can be seen to have a flash action in the flash evaporator after passing through the outdoor heat exchanger, the saturated refrigerant at the flash evaporation position can enter the enthalpy-increasing component through the single valve, and is mixed with the refrigerant discharged by the low-pressure-stage cylinder in the middle-pressure cavity communicated with the enthalpy-increasing component, so that the superheat degree of low-pressure-stage exhaust is absorbed, the supercooling degree of the refrigerant introduced into the indoor heat exchanger can be improved, the phase-change heat exchange coefficient is raised, and the refrigerating capacity is improved.

In order to understand the present solution more clearly, it is further explained below.

The enthalpy increasing technology mainly solves the problems of poor heating effect of the single-stage compressor in winter, large refrigeration attenuation in summer and the like. The heat pump air conditioner has the characteristics of high efficiency, cleanness, no pollution and the like, has huge market demand, can meet the use requirements of various systems by combining new refrigerants except R32 and R410a, is widely applied to the fields of household air conditioners, multi-split air conditioners, dehumidifiers, low-temperature heat pump water chilling units, heat pump water heaters, heating air heaters, freezing and refrigerating and the like, has an ultra-large operation range and high operation stability requirements, and therefore requires the two-stage enthalpy-increasing compressor to keep high performance under variable working conditions. The compressor pump has the outstanding characteristics that when the compressor pump is in a heating working condition, the throttling mode of single-stage compression is changed into a two-stage throttling middle incomplete cooling mode, so that the exhaust temperature is reduced, the flow of a refrigerant is increased, the pressure ratio reduction caused by two-stage compression is reduced, the leakage can be reduced, the volumetric efficiency is greatly improved, and the utilization efficiency of the compressor pump body under an extreme working condition is greatly improved.

The compressor sucks in low-temperature and low-pressure refrigerant through the liquid separator, the refrigerant is compressed in the low-pressure stage cylinder and then discharged into the medium-pressure cavity, and the refrigerant is fully mixed with the medium-pressure gaseous refrigerant sucked into the flash evaporator at the enthalpy-increasing part, sucked into the high-pressure stage compression cavity and compressed and then discharged.

As mentioned above, the two-stage enthalpy-increasing compression system pumps part of the branch liquid refrigerant from the main path by the flash evaporation effect of the flash evaporator, and the refrigerant in the main path is subcooled and the refrigerating capacity is increased due to the heat absorption process when the liquid refrigerant is gasified and absorbs heat under the intermediate pressure; however, when the low-temperature heat pump runs under the working condition of long-term low-temperature heating, the supercooling degree of the refrigerant in the evaporator is too low, so that the low-pressure stage compression cavity sucks the refrigerant mixed with liquid and gas for a long time, and when the mixed refrigerant is compressed, the liquid refrigerant cannot be compressed, and a part of the working volume of the compression cavity is occupied, so that the compression efficiency is influenced; meanwhile, liquid refrigerant can expand in the compression cavity due to the compression of liquid, the liquid impact phenomenon occurs, the following motion of the sliding sheet and the piston is impacted, and finally the sliding sheet is separated from the piston. The separation phenomenon is mostly caused when the running frequency of the compressor is higher, the communication of the compression cavity of the air suction cavity brought by the separation influences the refrigerating output, and simultaneously, huge abnormal sound and the abrasion of a moving part are aggravated. The compressor runs in the environment for a long time, performance fluctuation and noise brought by the compressor are a great problem which troubles the development of a two-stage enthalpy-increasing technology, the phenomenon can occur in a low-pressure-stage compression cavity, the high-pressure-stage compression cavity is also difficult to stabilize the liquid level of a flash evaporator due to the use of a two-stage throttling middle incomplete cooling mode, gas and liquid are very easy to supplement, and the sliding vane piston separation phenomenon can also occur. And from the operating pressure difference, the pump body structure of the double-stage air-supply enthalpy-increasing compressor divides the high pressure ratio of the original single-stage compression into the low pressure and the high pressure corresponding to the compression of the two compression cavities, so that the pressure ratio is decomposed, the condition of large leakage amount under the original single-stage compression high pressure ratio can be improved under the double-stage compression, but under the condition that the pressure ratio in the compression cavities is too small, so that the back pressure (namely the high pressure discharged by the compression cavities) of the sliding sheet is too low relative to the pressure ratio of the suction cavities, the phenomenon of separating from the piston is more easily generated due to insufficient back pressure.

In the conventional single-stage compressor, in order to solve the problem of sliding vane separation caused by air suction and liquid entrainment, a sliding vane embedded structure that the sliding vane is not separated from a piston is used, and the problem that the sliding vane is separated under the condition of liquid impact is solved. After dissecting embedded structure, can use on tonifying qi increases enthalpy compressor, its characterized in that: the structure is provided with at least one compression cavity, and the volume ratio of a low-pressure stage compression cavity to a high-pressure stage compression cavity of the enthalpy-increasing compressor is 0.5-1.2. The piston is driven to rotate along with the crankshaft, the sliding sheet embedded into the piston is driven to reciprocate in the sliding sheet groove of the air cylinder by the cooperative motion of the piston and the piston swings under the combined action of the driving of the crankshaft and the constraint of the sliding sheet. The piston and the sliding sheet are all embedded to form a moving mechanism, the movement of the moving mechanism is not different from that of a conventional structure, but the sliding sheet does not have the risk of separation under the embedding action of the sliding sheet and the piston, and the tail part of the moving mechanism does not need a spring to provide force for pressing the outer circular surface of the piston, so the operation stability of the moving mechanism is ensured by the rigidity of materials at the embedding part of the sliding sheet and the piston, and the moving mechanism has quality change compared with a mode that a spring with a conventional structure generates flexible variable force to ensure the long-term motion stability, not only the operation stability of the moving mechanism, but also the load attached to a crankshaft by the moving piece is small, and therefore the tail gas force of the moving mechanism is the key for balancing the moving system.

The vapor-supplementing enthalpy-increasing compressor discharges a refrigerant into the medium-pressure cavity after compressing the refrigerant through the evaporator introduced into the liquid separator, and a saturated gaseous refrigerant flashed by the flash evaporator after the first-stage throttling valve is mixed with the refrigerant and then enters the high-pressure cavity for compression, so that the high-temperature high-pressure refrigerant is discharged. In the above description, the supercooling degree of the refrigerant is an important index for balancing the enthalpy difference of the refrigerant, the condensed high-pressure supercooled liquid refrigerant enters the two-phase region after being subjected to primary throttling, one part of the condensed high-pressure supercooled liquid refrigerant is flashed in the flash evaporator into medium-pressure gaseous refrigerant, and the heat of the refrigerant which is not flashed is absorbed by the refrigerant in the flashing part, so that the liquid in front of the secondary throttling valve is supercooled, and the refrigerating capacity is increased. However, incomplete heat exchange of the evaporator caused by supercooling of liquid in front of the secondary throttle valve can cause that the refrigerant entering a liquid separator of the compressor is still in a gas-liquid mixed state, and the mixed refrigerant in a two-phase region in a thermodynamic state is a mixture which cannot be completely separated into a gas state and a liquid state by the liquid separator. When the low-pressure stage compression cavity compresses the liquid-state refrigerant, the efficiency of the first-stage compression is affected, so that the enthalpy difference of the refrigerant discharged by the first-stage compression is lower than that of the refrigerant discharged after the pure gas-state refrigerant is compressed, therefore, when the refrigerant is mixed with the saturated gas-state refrigerant introduced by the enthalpy increasing component in the middle-pressure chamber, the refrigerant state is poor, the exhaust temperature of the refrigerant discharged after the high-pressure chamber compresses the refrigerant is low, the system heat exchange efficiency is poor, the reaction is linked, the comprehensive energy efficiency is almost the same as that of the single-stage compression, and the system efficiency is low. When the situation is aggravated, the refrigerant discharged from the low-pressure stage compression cavity also contains liquid refrigerant, the refrigerant supplemented by the enthalpy increasing component in the medium-pressure cavity brings more liquid refrigerants due to unstable liquid level of the flash evaporator, the temperature of the refrigerant discharged after the mixed refrigerant is compressed by the finally generated high-pressure cavity is too low, the discharged refrigerant contains a large amount of lubricating oil mutually soluble with the refrigerant due to low viscosity of the compressor lubricating oil caused by low exhaust temperature, and when the lubricating oil enters a pipeline of an external heat exchanger, the heat exchange efficiency is poor, and the phenomenon appears circularly until the capacity of the compressor and the heat exchange capacity of a system are kept balanced. The compressor running in the state has low compression power and poor system heat exchange capacity, and the overall performance is greatly reduced.

However, the double-stage enthalpy-increasing compressor is originally designed for improving the low-temperature refrigerating capacity, and the operation range of the double-stage enthalpy-increasing compressor is more emphasized than that of a single-stage compressor in the long-term operation under the liquid-carrying working condition and is only limited to the working condition in some new refrigerant systems. When the compressor runs under the working condition for a long time, the problems of loss of moving parts, noise, running fluctuation and service life caused by liquid impact are always the problems which bother the double-stage enthalpy-increasing compressor. Through combining gleitbretter embedding piston, can solve wherein more outstanding motion piece and break away from the problem, and through the structural style of gleitbretter embedding piston, brought the great expansion of compressor on original operating range.

The embedded structure of gleitbretter has increased the sealed distance of gleitbretter head, and when compression band liquid refrigerant, the high-low pressure chamber that gleitbretter and piston are separated can not reveal from the gleitbretter head under the effect of hydraulic shock, and for conventional structure, its sealed distance is sealed by the single line and is become the double-line and seal. Theoretically, when the machining of the sliding sheet head meets the use requirement, the head of the sliding sheet can generate two corresponding contact points in the axial direction after being combined with the embedding groove of the piston during operation, the two contact points change along with the change of the operation angle of the crankshaft, and the relative positions of the two contact points are not fixed or opposite; secondly, when a conventional structure operates, the contact point (in the axial direction) operation leakage generated between the sliding vane head and the piston contact surface changes along with the change of the crankshaft operation angle, and the leakage amount calculated from the time domain is about 5 percent of the volume of the compression cavity; thirdly, after the hinge structure is applied, the time domain leakage amount of the two-point seal (in the axial direction) is 5% by 5% or 5% by 0.25% under the condition that the low pressure and the high pressure of the compression cavity are not changed, and the brought head leakage amount is reduced by more than 20 times; in the middle pressure part between two points (relative to the high pressure and the low pressure of the compression cavity), the relative pressure ratio is smaller than the high-low pressure ratio, so the single-point time domain leakage amount is between 1% and 2%, and the actual time domain leakage amount is almost trace.

Second, structurally, the use of a slip sheet embedded structure eliminates the risk of detachment relative to conventional structures. In conventional structure, the high pressure at spring and gleitbretter back is the main power that keeps the gleitbretter head to follow piston motion all the time, but when compression takes liquid refrigerant, liquid refrigerant can absorb compression chamber compression consumption and take place gasification and inflation, the gasification process is invariable static expansion process, when expanding in the compression chamber that the volume reduces, not only can take away the heat in the compression chamber, liquid refrigerant can not expand completely simultaneously, produced expansion volume can long-pending stay in the compression chamber, produce the attack to the fragile position in compression chamber. Therefore, in the conventional structure, the pressing force on the slide piece, which is ensured by unstable spring force and unstable gas force, cannot resist the reverse separation force generated by the slide piece impacted by liquid, and the slide piece repeatedly separates and impacts the piston along with the time domain, thereby showing the rattling noise and the fluctuation of the refrigerating capacity during operation. After the sliding vane is replaced into an embedded structure, the force for ensuring the sliding vane to compress the piston is replaced by the rigidity of the material at the embedded part of the sliding vane head and the piston, the upper limit value of the fracture moment of the material is far higher than the change force caused by the impact of liquid refrigerant, the separation risk is avoided in the actual operation, the risk of exciting the vibration mode of the compressor by the impact of the liquid impact force in a compression cavity is avoided, and the operation stability and the service life are obviously improved.

Finally, the back pressure problem of the sliding sheet caused by the high pressure ratio of single-stage compression is solved by the double-stage enthalpy-increasing compressor, no matter the low-pressure-stage compression cavity or the high-pressure-stage compression cavity adopts a hinged structure, the separation problem caused by insufficient gas force at the back of the sliding sheet does not exist, the reduction of the refrigerating capacity caused by the communication of the compression cavities caused by the change of the separation times in the operation time domain from the conventional structure to the hinged structure is attenuated to 0, and from the viewpoint of system operation, the constant refrigerating capacity effect and the stable exhaust temperature effect generated by the change are reflected in that the oil content of the refrigerant discharged by the compressor is reduced, and the heat exchange capacity of the system is improved; the refrigerating capacity of the compressor is not fluctuated, and the system can be more obviously embodied in the aspects of long-term running power consumption and the running life of a moving part.

From the macroscopic view, the sliding sheet separation phenomenon during the operation of the air-supplying and enthalpy-increasing compressor is improved, the phenomenon of air suction and liquid carrying during compression cannot be directly eliminated, but through the stable operation of the compressor, the system can block the condition for reducing the heat exchange of the system, the working input and the heat exchange condition of each heat exchange component are stable, the liquid level of a flash evaporator is stable, most of refrigerant supplemented from the flash evaporator is in a gas state, the stable gas state can be maintained when the refrigerant is mixed with the refrigerant discharged from a low-pressure stage in an intermediate cavity and then is sucked by a high-pressure stage compression cavity, the condition of the liquid refrigerant in a compression zone cannot occur in the high-pressure cavity, the exhaust temperature of the compressor is reduced, the heat exchange effect of the system is deteriorated, the performance of the compressor under the liquid carrying condition can be fully exerted by the forward circulation, the heat exchange effect of the system cannot reduce the heat exchange coefficient of the system due to the high oil discharge rate caused by the compressor under the liquid carrying condition, the long-time stable operation under the low-temperature or ultralow-temperature condition is realized, and the high performance of the compressor is maintained so as to meet the use requirements of users.

From the thermodynamic perspective, the theoretical isentropic compression power of the compressor during operation can be changed due to the physical state and the thermodynamic state of the compressed fluid, and the theoretical isentropic compression cycle power can be directly improved by changing the physical state and the thermodynamic state of the compressed fluid. When the compressor operates under the working condition of liquid, the refrigerant supplemented from the flash evaporator needs to be mixed with the gas discharged after the low-pressure stage compression before entering the high-pressure stage compression cavity, and the refrigerant supplemented from the flash evaporator absorbs the heat of the refrigerant discharged from the low-pressure stage in the process, so that the liquid in front of the secondary throttling valve is supercooled, the enthalpy difference value of the two-stage compression is increased, and the refrigerating capacity is increased. In the above cycle, when the mixed refrigerant is compressed by the high-pressure stage, the refrigerant discharged after being compressed by the high-pressure stage is overheated due to the stable refrigerant state supplemented by the flash evaporator, the supercooling degree of the refrigerant before the second-stage throttle valve is increased, the suction superheat degree of the low-pressure stage compression cavity is increased, the compressed liquid is supercooled, the isentropic compression process of the refrigerant in the compression cavity is not established during the low-pressure stage compression, the sucked refrigerant state during the high-pressure stage compression is influenced, the temperature of the refrigerant discharged after being compressed by the high-pressure stage is reduced, the influence is expanded into the system, the compression efficiency of the compressor is influenced in a circulating reciprocating manner, and the overall energy efficiency of the compressor is reduced. In conclusion, the sliding vane embedded structure is used for a low-pressure stage or a high-pressure stage, the fluctuation of refrigerating capacity of the compressor in a time domain caused by the separation of the sliding vane can be eliminated, the temperature of a refrigerant discharged after the compression of the high/low-pressure stage can be raised by the structure, and finally, more refrigerant heat can be absorbed when the refrigerant is mixed in a middle pressure cavity of the compressor due to the stable lifting of the heat exchange coefficient of the system and the stable state of a flash evaporator flash refrigerant, so that the supercooling degree of the liquid in front of a secondary throttle valve is improved, the refrigerating capacity is increased, the beneficial circulation reciprocating effect on the system is realized, the system energy efficiency of the air-supplementing enthalpy-increasing compressor using the sliding vane embedded structure is improved, and the task of meeting the requirement of the compressor on energy efficiency lifting under the extreme working condition is achieved.

Structurally, gleitbretter embedding piston structure has the refrigerating output to be stable, the problem that no sound phenomenon brought of dazzling, simultaneously because gleitbretter head inlays the back with the piston, the gleitbretter can not paste tight gleitbretter groove like conventional structure unilateral under the effect of compression chamber pressure differential, but be oblique line formula and span about the gleitbretter, the lifting surface area has not only been reduced, simultaneously because this structure can effectively block the outside passageway of revealing of high pressure side direction, it also is less than conventional structure to reveal the volume from cylinder gleitbretter groove. And the tail part of the sliding sheet does not need spring force and high-pressure gas force as running guarantee, the requirement on a moving part is greatly reduced, great help is provided for the time domain running integrity and a balance system of the compressor, and the influence on the noise vibration and the running life of the compressor is very important. In a conventional structure, when the arc of the sliding sheet head part runs to the end of exhaust, the clearance volume at the exhaust side is communicated with the clearance volume at the suction side, so that the clearance volume at the high-pressure side is expanded in the suction cavity, the volume of the suction cavity at the low-pressure side is occupied, and the compression efficiency is influenced.

The characteristics are combined with the enthalpy increasing technology, the advantages are not limited to stable refrigerating capacity and no sound, the structural characteristics need to be adjusted according to the enthalpy increasing compressor, and the change is as follows:

compared with the conventional structure, the compressor cylinder has no exhaust inclined notch, because the clearance volume exists and in the conventional structure, when the crankshaft moves to an exhaust end position, the arc at the head part of the sliding sheet and the piston can exhaust the last volume from the exhaust inclined notch, namely, when the crankshaft moves to the tail, no axial volume exists outside the chamfer at the sliding sheet groove of the cylinder, and therefore all gas in the compression cavity needs to be exhausted from the exhaust inclined notch; and in order to ensure that the exhaust port at the radial end cover has a certain distance with the air suction port as much as possible, the air cylinder prevents air suction from flowing back, and the exhaust port surface of the radial end cover cannot cover the volume. However, in the sliding vane embedded structure, when the crankshaft rotates to the initial position (i.e. the exhaust end position, the suction opening position), there is an unclosed cavity between the inner cylinder wall and the exhaust side wall of the sliding vane and the exhaust side wall of the piston, which are arranged outside the chamfer of the sliding vane slot of the cylinder, and the cavity does not decrease with the rotation of the crankshaft to the suction area, but the volume is reserved in each exhaust process. Through the exhaust scarf of cancellation cylinder, this region can discharge last some exhaust volume from compression chamber, reduces this volume department high pressure refrigerant and flows back to and expand again in the lower compression chamber of pressure, avoids the gas compression theory isentropic power reduction because of gas over compression produces to reduce pump body efficiency. When the structure is applied to an enthalpy-increasing compressor, the structure is more suitable for a scene that the relative pressure ratio of the enthalpy-increasing compressor is reduced when a single-stage compression ratio is split into two-stage compression, the exhaust resistance loss is reduced compared with a single-stage compressor due to the fact that the relative pressure is at least half lower than that of the single-stage compressor, and the final reduced overpressure power reaches 33% -67% (for a pump body structure of the two-stage enthalpy-increasing compressor applying a hinged structure, an air cylinder is arranged without an exhaust oblique notch, the mechanical loss is directly reduced by canceling the clearance volume of the exhaust oblique notch at the exhaust port, when a hinged piston and a sliding vane move to the end of compression, the peripheral surface of the piston, the side surface of the sliding vane and the inner surface of the air cylinder surround a certain volume, the volume directly affects the clearance volume, the volume is larger than that of a conventional structure, the overall clearance volume at the exhaust port is larger than that of the conventional structure, the performance of a compression cavity using the hinged structure is affected, the exhaust port oblique notch is cancelled, the influence caused by the large clearance volume of the large clearance volume generated by using the hinged structure is directly reduced, and the exhaust resistance loss is reduced when the hinge structure is arranged without the exhaust pressure loss and the exhaust pressure loss, the hinge loss is reduced. And because the single-stage compression of the enthalpy-increasing compressor is changed into double-stage compression, the occupation ratio of the total exhaust loss and the over-compression power in the work loss of the compressor is far higher than that of the single-stage compressor, and the isentropic compression power of the lifting theory is obviously improved.

In the conventional structure, when the piston moves to the air suction initial position, the compression cavity is used as an air suction cavity, air is sucked from the air suction port to be compressed, a distance is inevitably arranged between the air suction port and the sliding sheet groove, and the phenomenon that the exhausted high-pressure air flows back to the air suction port from the sliding sheet groove to influence the compression efficiency is avoided. Viewed from the axial direction: when the contact point of the piston and the cylinder rotates gradually from an initial angle (0 ℃) until the contact point finally reaches the air suction port area, a communication channel is not formed with the air suction port all the time, so that the volume enclosed by the piston, the cylinder and the sliding sheet in the axial direction is continuously increased, the vacuumizing phenomenon is caused, and the suction volume can be occupied by the vacuumizing phenomenon; when finally connected to the suction port, the pressure difference causes pressure pulsation, and a suction chamber backflow phenomenon occurs with the vane groove. Through set up the side cut on the piston, the evacuation in this region shows to be eliminated, can and only can set up this side cut in gleitbretter embedded structure inspiration side, can not produce because the piston can produce around the relative rotation of bent axle eccentric part and set up the side cut in the conventional structure. And because the slide sheet is sealed with the left side and the right side of the cylinder slide sheet groove under the action of high-low pressure difference, fluid can not enter the trimming channel from the slide sheet groove to cause leakage. Under the influence of the trimming, the suction pulsation of the pump body is reduced, the suction resistance loss is reduced, the suction leakage is reduced, and the brought influence is more obviously embodied in the enthalpy-increasing compressor which is converted from single-stage compression to double-stage compression. The suction port of the double-stage enthalpy-increasing compressor is doubled compared with single-stage compression, the suction loss and the leakage risk of the double-stage enthalpy-increasing compressor are far larger than those of the single-stage compression, and the edge cutting structure can reduce 15% -39% (in the compression process of the conventional structure, no matter how the suction port is arranged, when the piston runs from the top point of the sliding sheet head to the opening angle of the suction port, a compression cavity formed by the piston, the sliding sheet and the inner wall of the cylinder can generate a vacuumizing phenomenon, when the compression cavity is connected to the suction port, pressure pulsation at the suction port can be caused due to pressure difference in the compression cavity, and because the hinged structure is provided with the edge cutting at the piston and the suction port, the compression cavity can be always communicated with the suction port in the state, the vacuumizing in the suction process is avoided, the suction pulsation loss is reduced, and the occupation ratio of the pressure pulsation loss in the indicated power is reduced), so that the influence on the fluid loss is more obvious.

In conclusion of the two structural characteristics, when the sliding vane embedded enthalpy-increasing compressor is combined for application, the structural change, pulsation increase, suction and exhaust loss increase and low mechanical efficiency caused by the fact that single-stage compression is converted into double-stage compression can be greatly reduced, meanwhile, in the application field of the enthalpy-increasing compressor, the requirements for mechanical loss under the working conditions of large pressure difference and large pressure ratio are improved, the requirement for indicating power loss is guaranteed not to be suddenly increased due to the change of heavy working conditions, the compressor stands at the angle of reliability, the influence of leakage loss under the heavy working conditions on the indicating power loss is the largest, the sliding vane separation phenomenon can be avoided by using a hinged structure, the indicating power loss is reduced from the leakage, and the requirement under the heavy working conditions is met; on the other hand, from the mechanical loss perspective, the hinge structure has great advantages for the whole running power dissipation because the tail part does not need to increase the spring force or the internal back pressure of the compressor, not only does not increase the mechanical loss of the compressor in running, but also can reduce the problems of unstable running and the running life of the compressor in running under heavy working conditions, and meets the reliability and the stability of the compressor in full-load running under severe working conditions in time domain. The performance of the compressor is widened from the time domain through the operation power consumption, the operation stability, the operation service life and the like of the compressor, not only is the improvement of the operation range reflected, but also the refrigerants used by the compressor can be greatly increased, such as some new refrigerants which are not commonly used in a rotor compressor, and the application field of the rotor compressor is greatly improved and the application range of the rotor compressor is widened by combining with new systems such as refrigeration, air heaters and the like.

Meanwhile, the two-stage air-supply enthalpy-increasing compressor with the sliding-vane embedded structure can be used for designing a new-generation pump body, and can be used for realizing new directions which cannot be realized in the original conventional structural design by adjusting various parameters of the compressor.

The motor circulation hole area is not less than the compression chamber working volume, and the significance lies in: when the compressor displacement increases, its working area for the compression chamber not only needs the exhaust flow of compressor when the operation, still needs the compression stability when satisfying high-speed operation, synthesizes promotion compression operation noise, vibration and performance when compressing big displacement design.

The motor is a concentrated coil, and the concentrated coil motor is more beneficial to the expansion of a large-displacement design of the compressor under the condition of not replacing a series; the motor of the concentrated coil is used because the motor has more excellent performance and better compatibility with a household air conditioning system, and the cost, noise and vibration of the motor can meet the requirements of a compressor on a power source when the compressor is designed to be high-speed and small-sized.

On the other hand, the arrangement of a middle pressure cavity of the air-supplementing enthalpy-increasing compressor is also important for the influence of the air-supplementing effect, the middle pressure cavity is a working volume in which a high-pressure supercooled liquid refrigerant after being subjected to primary throttling is reduced to a middle pressure and enters a two-phase region, wherein a part of the flashed middle-pressure gaseous refrigerant and the refrigerant discharged from a low-pressure stage are mixed, and the volume of the middle-pressure cavity in the working volume cannot meet the requirement that the liquid-carrying refrigerant introduced into the condenser and the gaseous refrigerant discharged from a first-stage compression cavity are fully mixed, so that very large air flow pulsation is caused, and the performance of the compressor is influenced; meanwhile, two refrigerants with different supercooling degrees are completely mixed in the medium-pressure cavity, so that the improvement of the flow of the secondary-compression refrigerant is vital, and when the structural parameters of the compressor cannot be improved, the improvement of the flow of the secondary-compression refrigerant is particularly important for improving the indicating efficiency of the compressor.

Therefore, aiming at the air-supplementing enthalpy-increasing compressor with the sliding vane embedded structure, the guarantee force for the following motion of the piston and the sliding vane is the material rigidity of the component, unstable gas pressure is not needed to provide power to guarantee that the sliding vane is not separated from the piston, the conventional pump body structure can be changed, the original medium-pressure cavity is enlarged, and the air-supplementing enthalpy-increasing compressor is mainly characterized in that the gas force borne by the tail part of the sliding vane is the medium-pressure gas formed by mixing the gas replenished by flash evaporation and the refrigerant discharged from a low-pressure stage.

In the conventional structure, the arrangement of the medium-pressure cavity also affects the overheating loss and the mechanical loss, the high pressure at the tail part of the sliding sheet has great influence on the friction force of the sliding sheet during the operation of the conventional compressor, the friction power consumption of the compressor at the head part and the side surface of the sliding sheet generally occupies more than 1/3 of the whole operation power consumption through the analysis of the power consumption during the operation, the phenomenon that the sliding sheet is separated from a piston easily exists in the double-stage compression under certain pressure difference working conditions, and the operation performance and the stability of the compressor are greatly affected by the fluctuation of the refrigerating capacity and the noise vibration generated by the double-stage compression. Meanwhile, the middle pressure cavity does not help the overheating loss of the secondary compression cavity, the air suction temperature of the middle pressure cavity is determined by the temperature of the mixed gas in the middle pressure cavity, the middle pressure cavity does not have the effect of reducing the overheating loss in the primary compression, and the middle pressure cavity does not help the overheating loss in the secondary compression. The expansion of the medium-pressure cavity is beneficial to adjusting the temperature difference outside the two compression cavities into a sequential difference, the supercooling degree of the refrigerant in front of the second-stage throttling valve can be raised by absorbing the heat lost by the compression machinery of the low-pressure stage, the compression loss of the low-pressure stage can be reduced by recovering the heat lost, and the enthalpy difference value of the high-pressure stage sucked refrigerant is increased; meanwhile, the supercooling degree of the refrigerant before the secondary throttling valve can be raised by absorbing the heat lost by the high-pressure stage compression machinery, the compression loss of the high-pressure stage can be reduced by recovering the heat lost, the integral exhaust temperature rise of the two-stage air-supply enthalpy-increasing compressor with the sliding-vane embedded structure is reduced, and the reduced mechanical loss can be reused in the enthalpy difference value of the refrigerant; in addition, the relative pressure of the medium-pressure gas at the back of the sliding vane is opposite to that of the gas at the high-pressure stage and the low-pressure stage, after the stress of the sliding vane is analyzed, the medium-pressure gas can reduce the friction loss by 12.3% -15.9%, and the power loss during the operation of the compressor is comprehensively reduced. Because the subsidiary effect of this structural change is under some very extreme operating modes, if under the ultra-low temperature heating, can follow the gas pressure that supplys into in the flash vessel and promote, because the saturated refrigerant of flash vessel that can supply into in the middle chamber increases, its comprehensive efficiency can promote 2% -5% under this operating mode, and the adaptability and the efficiency promotion of compressor under the extreme operating mode all help.

In conclusion, when the medium-pressure cavity is arranged inside the shell, by combining the characteristics of the sliding vane embedded structure, the refrigerant flow, the leakage risk, the refrigerating capacity fluctuation, the overheating loss and the mechanical loss of the high-pressure/low-pressure stage compression cycle are greatly optimized, the indicated power loss of the two-stage compression is influenced, the theoretical isentropic compression power is improved, the operation efficiency of the compressor under the full working condition is improved, particularly the operation stability and the operation efficiency of the air-supplying enthalpy-increasing compressor under the heating working condition and the working condition with large refrigerating capacity are improved, the advantages of the two-stage compression compared with the single-stage compression are greatly improved, the indicated efficiency of the two-stage compression compared with the single-stage compression under the refrigerating working condition is also reduced, the efficiency of the single-stage compression under the light working condition can be more advantageous, and the application range of the compressor is widened.

Meanwhile, the characteristic requirements are also applicable to refrigerants with special physical properties, such as R32, R410a, R290, R607c, CO2, R1234a, R1234yf, R1234ze, R404a, R600a and the like, the performance advantages of air-supplementing and enthalpy-increasing can be better played in the double-stage air-supplementing and enthalpy-increasing compressor with the sliding-vane embedded structure, and meanwhile, the problems that the low-temperature refrigerating capacity fluctuates for a long time, the heating noise is large, the system effect is not obvious and the like which plague the field of the rotor compressor are solved, and the application range of the compressor is greatly enlarged.

Along with the motion of the crankshaft, the piston and the slip sheet are combined together through the cylindrical head of the slip sheet and the groove reserved at the corresponding position of the piston all the time without separation, and the piston and the slip sheet move in a combined mode that the slip sheet moves in a reciprocating linear motion in a cylinder slip sheet groove and the piston continuously swings along with the crankshaft. In the moving process, the piston and the sliding sheet are set by the structure of the embedded groove, so that the crankshaft can always follow the moving in the moving period under the rigidity of the groove, and the separation phenomenon cannot be generated.

Meanwhile, the thick line at the detail amplification position of the cylinder is the projection of an exhaust port arranged on an end cover (or a sealing surface of a bearing) in the axial direction of the cylinder, a piston and a sliding vane are driven by a crankshaft to move at a starting position (or an exhaust ending position) after being embedded, the projection at the position can be always in communication with a volume k axially enclosing the head side surface of the sliding vane, the cylinder side surface and the excircle side surface of the piston, the volume k is not changed into 0 because the crankshaft rotates to the air suction starting position (or the exhaust ending position), so that a compression cavity Ph which is continuously reduced along with the movement of the crankshaft is always communicated with the exhaust port, the elimination of a diagonal cut does not influence the fluid discharge in the compression cavity Ph, and in the subsequent movement, the volume of the volume k is continuously reduced along with the increase of the volume of an air suction cavity Pl, the process is completely different from the conventional structure, and the volume k is communicated with the air suction cavity Pl after the crankshaft rotates by an ending angle, so that the volume k is communicated with the Pl, and is essentially expanded compression cavity Ph, and the refrigerant occupies a working volume of the compression cavity Ph, so that the refrigerant is reduced in the compression cavity, and the refrigerant is compressed by the overpressure, and the overpressure of the compression cavity; after the sliding sheet embedded structure is replaced, the volume k can exhaust residual gas when air suction starts/air exhaust ends, the volume k is continuously reduced along with the increase of the air suction cavity Pl, and k is not completely 0 in the reduction process but is always communicated with the air exhaust port, so that in the movement process, the volume k can be reduced by about 30% -50% compared with the conventional structure, and the exhaust side clearance volume (or over-compression volume) is directly reduced by 60% -75% by combining with the elimination of the exhaust inclined notch; after the fluid resistance simulation is carried out on the flow passage, the power consumption loss caused by calculation to the clearance volume can be reduced by 1.79-2.03%, the power consumption loss is increased along with the increase of the volume of the actual working cavity of the compressor, and the isentropic compression power is improved.

Along with the rotation of the crankshaft, a contact point is generated on the side face of the excircle of the piston and the inner circle face of the cylinder due to the structural setting in the initial position, a volume j formed by enveloping the contact point towards the direction of the sliding piece and the side face of the sliding piece is an air suction cavity Pl, and in the movement process of the crankshaft, the volume j is in a state of volume expansion before the contact point moves to the range of the air suction port, so that after the contact point moves to the range of the air suction port, the volume j is communicated with the air suction port, and the continuously expanded volume j is used as the air suction cavity to start acting. In the above process, when the crankshaft does not operate to the position shown in the figure, the internal pressure of the volume j is the same as the pressure of the suction cavity Pl, when the crankshaft moves to the position shown in the figure, the channel with the suction cavity Pl is closed, and the volume j is continuously enlarged along with the moving volume of the crankshaft, so that the internal pressure is gradually reduced, when the crankshaft moves to be communicated with the suction port, the pressure in the volume j is increased, so that the pulsation of the suction pressure caused by the pressure increase affects the fluid resistance of the suction cavity during operation, and when the volume j is not communicated with the suction port, the working cavity is not included in the working range of the suction cavity, so that the working cavity is regarded as useless work, and the compression efficiency is not benefited.

The closed cavity j of the piston is opened when the crankshaft rotates to the initial position, the volume j can be communicated with the air suction port by cutting edges on the corresponding outer circular surface of the piston, the air suction pulsation and the invalid working cavity disappear due to the communication, the dispersion rate of the air suction resistance loss is reduced by 15%, meanwhile, the vibration loss of a moving part is reduced due to the fact that large pressure pulsation does not exist on the radial left side and the radial right side of the head of the sliding piece, and the motion mode and the vibration noise of the pump body are superior to those of the original scheme.

The sliding vane type embedding structure used in the attached drawing is only a schematic diagram, and is actually used in a two-stage air-supply enthalpy-increasing compressor, and the sliding vane type embedding structure is formulated at a low-pressure stage or a high-pressure stage or according to the use condition of a system when the sliding vane type embedding structure is actually used; the figures mainly show that the areas of the piston and the sliding vane which are contacted with the upper end cover and the lower end cover are equal in the low-pressure stage and the high-pressure stage. The contact distance between the upper end surface and the lower end surface of any one of the pistons and the contact distance between the upper end surface and the lower end surface of the upper end cover plate and the lower end cover plate sealed with the upper end surface of the lower end surface of the piston are different, and because the contact distance between the upper end surface and the lower end surface of the piston is different, oil liquid in the stable operation of the pump body is stable in all directions, the piston can float under the difference of the upper contact area and the lower contact area without considering the action of gravity, and in the actual operation, the gravity is balanced with the buoyancy, and the clearance value between the piston and the upper end cover plate is stable

Is smaller than the conventional structure, and has a clearance value with the lower end cover

The upper and lower clearance values are larger than those of the conventional structureThe upper gap value is larger in comparison. The above effect brings about the advantage that in the conventional structure, the upper gap value

Is much larger than the lower gap value

So that tip clearance loss and top clearance value are obtained during operation

Positive correlation, lower gap value

Because of too small, the critical oil film thickness is not satisfied after stable operation, so that the dynamic pressure lubrication of the oil liquid cannot be realized, and the friction loss is large. After the above improvement, the upper gap value

A smaller gap value is kept under the condition of meeting the dynamic pressure lubrication thickness, and the friction coefficient and the top gap leakage are met simultaneously; lower clearance value

The thickness of the oil dynamic pressure lubricating oil film is increased by several times compared with the conventional structure; the upper clearance value is larger than the lower clearance value, and the end face leakage mainly depends on the upper clearance value

The end face leakage of the piston is reduced overall, and the friction coefficient of the piston during movement is greatly reduced.

Similarly, the same effect can be produced by performing the above processing on the slide piece, but the proportion of the leakage amount at the top of the slide piece in the compression leakage loss is small, so that the radial friction coefficient of the slide piece and the friction coefficient increase and the jogging of the jogged moving piece caused by the inconsistency of the moving state when the slide piece is jogged with the piston are mainly improved, and the performance and the noise are influenced. The slide sheet and the piston can be applied to the moving part in pairs in the form of different upper and lower contact surfaces, and can also be used according to the design parameters of the pump body.

The connecting technology is combined with an air-supplementing and enthalpy-increasing technology, an enthalpy-increasing part is improved by combining two technical characteristics, the power loss during the operation of double-stage compression is solved, and the compression cycle efficiency is improved; meanwhile, structural improvement is carried out in the gas supplementing and enthalpy increasing field aiming at the hinged application characteristics, the compression efficiency of the compressor in the gas supplementing over-range operation is met, the problem of operation stability caused by liquid carrying of the gas suction of the compressor under the heating working condition is solved, and the operation performance of the compressor in the full range is improved. And through combining the design of articulated compressor parameters, the compressor meets the requirement of improvement according to high efficiency and miniaturization under the existing process conditions, the application range of the air-supplementing enthalpy-increasing compressor is comprehensively enlarged, and the compressor is suitable for new generation compressor technical breakthrough points such as new refrigerants, long service life and energy improvement efficiency.

In conclusion, the invention combines two technical characteristics, and solves the technical problems of liquid compression, gas supply, liquid entrainment and the like easily caused during the operation of the compressor according to the use characteristics of the compressor, thereby not only improving the capacity performance of the enthalpy-increasing compressor under a specific working condition, reducing the power consumption, but also prolonging the operation life of the compressor. The enthalpy-increasing compressor can bear more extreme working conditions, the operation capability under the extreme working conditions is guaranteed, and technical pain points such as large differential pressure in a conventional operation state are solved, so that a new technical means is provided for the problems of high differential pressure, high pressure ratio, low evaporation temperature, low condensation temperature and the like.

The invention aims at solving the problem generated after the two technical characteristics are combined, and improves the structure of the compressor from the operation efficiency, so that the two technical characteristics are improved, the use effect is improved, and the requirements of the compressor on operation stability, low noise, high efficiency and the like after the operation range of the compressor is exceeded are met. The common double-stage air-supply enthalpy-increasing compressor can not be compared with a single-stage compressor due to the problem of operation efficiency in light working condition operation, and has the advantage that the overall working condition operation effect caused by low-temperature heating quantity is improved. By solving the problems, the occupation ratio of the compressor in various losses is improved, the problem which puzzles the development of the double-stage compressor for a long time is solved, and the method is a more innovative middle-hardness direction of a new generation of double-stage enthalpy-increasing compressor technology.

Meanwhile, due to the development of the rotor compressor and the improvement of the use requirements of people, the evaluation dimensionalities of the performance, the noise, the reliability and the like of the compressor are continuously increased, the air-supplying enthalpy-increasing technology is combined with the hinge technology to be capable of carrying out miniaturization, high-speed and higher operation life design on the compressor on the premise of meeting the requirements, meanwhile, the characteristics of low noise and low cost of the compressor can be maintained, the compressor can be enabled to push more updated iterative products in the face of the challenge brought by the improvement of the use requirements of users, and the ever-increasing requirements on the future market are met.

The invention can solve the following technical problems: 1. the vapor-supplementing enthalpy-increasing compressor (namely the compressor) is easy to cause the problems of abnormal performance, noise and operation stability due to the compression of liquid in the heating process; 2. the air-supplying enthalpy-increasing compressor has limited heating capacity under the heating condition, and meanwhile, a new refrigerant puts higher requirements on the compressor; 3. the vapor-supplementing abnormality easily generated by the vapor-supplementing enthalpy-increasing compressor; 4. the middle pressure cavity of the air supply compressor is fixed without improvement points; 5. the clearance volume of the air-supplementing enthalpy-increasing compressor is large, compression, vacuum pumping and the like are easy to perform when compression starts and ends, and the energy efficiency is reduced; 6. miniaturization and high-speed design cannot be carried out, and the performance of the two-stage enthalpy-increasing compressor is further improved; 7. the vapor-filling enthalpy-increasing compressor has higher requirements on moving parts such as a spring, a sliding sheet and the like, and loss is easy to occur in the operation process.

The invention can produce the following beneficial effects: 1. the problems of abnormal performance, noise and operation service life caused by the compression of liquid in the operation process of the air-supplementing enthalpy-increasing compressor are solved; 2. the heating capacity of the air-supply enthalpy-increasing compressor under the heating condition is improved, and the adaptability of a pump body of the compressor to a new refrigerant is improved; 3. the problem of abnormal air supply easily generated by the air supply enthalpy-increasing compressor under an extreme working condition is solved, the theoretical air input of the secondary compression is expanded, and the energy efficiency of the compressor is improved; 4. the volume of the medium-pressure cavity is enlarged, so that the gas in the compressor can be fully mixed, the performance is improved, and the noise is reduced; 5. the clearance volume is reduced, so that the refrigerating capacity of the compressor is improved more obviously in the running process, and more energy is saved under the conventional working condition; 6. the air-supplying enthalpy-increasing compressor can be miniaturized and designed at high speed, and new requirements such as energy efficiency improvement and the like are met; 7. greatly reduces the use requirement on moving parts and greatly prolongs the service life of the compressor.

The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. A compressor, characterized by comprising a shell (10), an enthalpy-increasing component (20) and a plurality of compression parts (30) arranged in the shell (10), each compression part (30) comprising a cylinder (31) and a piston (32) and a slide vane (33) arranged in the cylinder (31), the plurality of compression parts (30) comprising a low-pressure compression part and a high-pressure compression part, the cylinder (31) in the low-pressure compression part having a low-pressure working chamber, the cylinder (31) in the high-pressure compression part having a high-pressure working chamber, the shell (10) having an intermediate-pressure chamber (11) therein, wherein the enthalpy-increasing component (20) and the intermediate-pressure chamber (11) are communicated, and the slide vane (33) in at least one compression part (30) is hinged with the corresponding piston (32); the volume ratio of the high-pressure working cavity to the low-pressure working cavity is 0.5-1.2, and the volume ratio of the medium-pressure cavity (11) to the low-pressure working cavity is more than 2; the cavity in the shell (10) is cylindrical, and the length of the shell (10) is more than or equal to twice the inner diameter of the shell (10); each of the compression parts (30) has a discharge port, and the sum of the areas of the discharge ports of the plurality of compression parts (30) has a value greater than the inner diameter of the casing (10); the cylinder (31) is provided with an air suction port, the outer wall of the piston (32) is provided with a tangent plane (321), and an air suction area (34) communicated with the air suction port is formed in an area among the tangent plane (321), the sliding vane (33) and the inner wall of the cylinder (31); the compressor also comprises a crankshaft (40), the pistons (32) of the plurality of compression parts (30) are sleeved on the crankshaft (40), the distance between the axis of the crankshaft (40) and the axis of the pistons (32) is an eccentricity A, the crankshaft (40) comprises a long shaft and a short shaft, the diameter of the long shaft is 2A-3A, and the diameter of the short shaft is 2A-2.5A; at least one of the sliding pieces (33) of the plurality of compression parts (30) comprises a first plate body (331) and a second plate body (332) which are connected with each other, wherein the end of the first plate body (331) is matched with the piston (32), and the second plate body (332) is matched with the sliding groove of the cylinder (31); the second plate (332) has a size smaller than that of the first plate (331) in an axial direction of the cylinder (31); the ratio of the thickness of the piston (32) to the inner diameter of the housing (10) is delta, and the height difference between the cylinder (31) and the piston (32) is greater than or equal to 3 delta and less than or equal to 4 delta.

2. Compressor, according to claim 1, characterized in that the sliding vane (33) of each compression portion (30) is hinged to the corresponding piston (32); wherein, piston (32) have the holding tank, the one end of gleitbretter (33) with the articulated cooperation of holding tank, the other end of gleitbretter (33) is located in the spout of cylinder (31).

3. The compressor of claim 2, wherein the compression portion (30) further comprises a bearing fitted to an end surface of the cylinder (31), the bearing having a discharge port; the exhaust port intersects the inner circle of the cylinder (31) on a projection of a radial cross section of the cylinder (31).

4. The compressor of claim 1, wherein a ratio of a height of the cylinder (31) to an inner circle diameter of the cylinder (31) is 0.5 or more.

5. Compressor according to claim 1, characterized in that the compression part (30) comprises an upper end cover and a lower end cover, the cylinder (31) being located between the upper end cover and the lower end cover, wherein,

the contact area between the upper end surface of the piston (32) and the upper end cover is B, the contact area between the lower end surface of the piston (32) and the lower end cover is C, and B and C are not equal; and/or the presence of a gas in the gas,

the contact area of the upper end face of the sliding piece (33) and the upper end cover is D, the contact area of the lower end face of the sliding piece (33) and the lower end cover is E, and D and E are not equal.

6. Compressor according to claim 1, characterized in that said intermediate pressure chamber (11) is located in the area between said plurality of compression sectors (30) and the inner wall of said shell (10), the outlet of said low pressure compression sector communicating with said intermediate pressure chamber (11) and the inlet of said high pressure compression sector communicating with said intermediate pressure chamber (11).

7. The compressor of claim 6, further comprising a motor (50) and an oil return pipe, wherein the motor (50) is in driving connection with the plurality of compressing units (30), a discharge chamber (12) is formed between the upper side of the motor (50) and the inner wall of the shell (10), an oil sump (13) is formed between the lower portions of the plurality of compressing units (30) and the inner wall of the shell (10), the oil sump (13) is spaced apart from the medium pressure chamber (11), a discharge port of the high pressure compressing unit is communicated with the discharge chamber (12), and the discharge chamber (12) is communicated with the oil sump (13) through the oil return pipe.

8. An air conditioning system, characterized in that it comprises a compressor according to any one of claims 1 to 7.