Pump body assembly, compressor and air conditioner refrigerating system

Abstract

The invention provides a pump body assembly, a compressor and an air conditioner refrigeration system.The pump body assembly comprises an air cylinder and a plugging piece assembled on the first end face of the air cylinder, a valve groove is formed between the plugging piece and the air cylinder, an air supplementing opening communicated with the valve groove is formed in the plugging piece, and a backpressure channel and an air injection channel are formed in the air cylinder; an air supply opening and closing valve plate is arranged in the valve groove, the air supply opening and closing valve plate is provided with an air supply position enabling the air supply port to be communicated with the valve groove and a back pressure position enabling the air supply port to be disconnected from the valve groove, and the air injection channel comprises a first air injection channel and a second air injection channel; a first air supply inlet of the first air injection channel and a second air supply inlet of the second air injection channel are arranged in a mirroring mode relative to the geometric center of the air supply opening and closing valve plate. The eccentric wear phenomenon of the air supply opening and closing valve plate in the opening and closing process is reduced, the position switching of the valve plate is more stable and reliable, the impact noise is reduced, and the opening and closing reliability of the valve plate is improved.

Description

Technical Field

[0001] The present invention belongs to the technical field of air conditioning, and particularly relates to a pump body assembly, a compressor, and an air-conditioning refrigeration system. Background Art

[0002] With the continuous expansion of the applicable range of low-temperature heat pump models and the gradual decrease of the application scenario temperature, the reliability requirements for heat pump units in low-temperature environments are getting higher and higher. However, the existing heat pump technologies mainly face pain points such as low heating capacity in low-temperature environments.

[0003] In view of the above-mentioned difficulties, a variety of jet-enhanced enthalpy structure compressors have been disclosed in the prior art. Currently, there are mainly two major mainstream technical routes:

[0004] The first technology (as shown in Figure 1 ): A jet valve seat is arranged on the exhaust port side of the cylinder, and a tongue reed valve plate is installed. When the pressure in the compression chamber is lower than the pressure at the jet port, the valve seat opens unidirectionally; otherwise, it closes. In this technology, the tails of the jet valve plate and the baffle are fixed to the cylinder by locking screws, that is, the tails are fixed, while the heads of the baffle and the jet valve plate are in a free state. This design has problems such as complex installation, large clearance volume, poor reliability of the air valve, and complex jet flow path with large flow resistance, seriously affecting the performance of the compressor. Especially for small series compressors, the installation is limited and the application is difficult.

[0005] The second technology (as shown in Figure 2 ): Jet holes are arranged at the compressor bearing or the intermediate partition of a twin-cylinder compressor, and the rotation movement of the roller is used to control the opening and closing of the jet port. This technology is limited by the opening angle range of the jet port, resulting in insufficient jet volume. In addition, when the jet-enhanced enthalpy function is turned off, some refrigerant will flow back from the compression chamber through the jet port during the cylinder compression process, resulting in partial cold loss and making the compressor do some useless work, thereby reducing the energy efficiency of the compressor.

[0006] In order to overcome the above-mentioned deficiencies, a circular valve is disclosed in the prior art to be arranged in the air supplement and enthalpy increase channel (such as the technical solution disclosed in the patent document with the publication number CN118775282A) to realize a structure for controllably supplementing medium-pressure air flow into the compression chamber by using the pressure difference between the two end faces of the circular valve. However, during the application process, the inventor found that the circular valve or the valve groove is severely eccentrically worn during the opening and closing process of the air supplement and enthalpy increase structure with the circular valve, which results in a large impact noise of the circular valve during the operation of the compressor and reduces the opening and closing reliability of the circular valve. Summary of the Invention

[0007] Therefore, the present invention provides a pump body assembly, a compressor, and an air-conditioning refrigeration system, which can overcome the technical problems in the related art that the air intake opening and closing valve plate in the air intake and enthalpy increase channel of the pump body assembly has serious partial wear of the valve plate or valve groove during application, resulting in relatively large impact noise of the round valve during the operation of the compressor and reduced reliability of the valve plate opening and closing.

[0008] To solve the above problems, the present invention provides a pump body assembly, including a cylinder and a plugging member assembled on the first end face of the cylinder. A valve groove is formed between the plugging member and the cylinder. An air intake opening is formed on the plugging member, and the air intake opening is communicated with the valve groove. A back pressure channel communicating with both the compression chamber of the pump body assembly and the valve groove is formed in the cylinder. A jet channel communicating with both the compression chamber and the valve groove is also formed in the cylinder. An air intake opening and closing valve plate is arranged in the valve groove. The air intake opening and closing valve plate has an air intake position for communicating the air intake opening with the valve groove and a back pressure position for cutting off the communication between the air intake opening and the valve groove. The air intake opening and closing valve plate realizes the switching between the air intake position and the back pressure position under the action of the pressure difference between its two end faces. The jet channel includes a first jet airway and a second jet airway. The first air intake of the first jet airway and the second air intake of the second jet airway are arranged symmetrically with respect to the geometric center of the air intake opening and closing valve plate.

[0009] In some embodiments, an annular groove is formed at the notch of the valve groove, the annular groove surrounds the air intake opening, and the air intake opening and closing valve plate is in clearance fit with the valve groove.

[0010] In some embodiments, both the first air intake and the second air intake are formed on the first end face and projected on the bottom wall of the valve groove. The first air intake and the second air intake respectively have an intersection with the annular groove; and / or, the air intake opening and closing valve plate is a circular valve plate, and the valve groove and the annular groove are concentric circular grooves.

[0011] In some embodiments, the suction volume of the pump body assembly is V, and the flow area of the annular groove is S, where 0.3 ≤ S / V ≤ 3.

[0012] In some embodiments, the first jet airway and the second jet airway are arranged symmetrically with respect to the central symmetry plane of the back pressure channel.

[0013] In some embodiments, the first jet airway has a first jet opening on the inner wall of the cylinder of the cylinder, and the second jet airway has a second jet opening on the inner wall of the cylinder of the cylinder. When projected on any radial plane of the pump body assembly, the center line of the jet path of the first jet opening and / or the second jet opening passes through the center point of the cylinder.

[0014] In some embodiments, the first air injection channel has a vertical section extending along the axial direction of the cylinder and an inclined section extending obliquely along the side close to the compression chamber. The vertical section is communicated with the inclined section, and one end of the vertical section far from the inclined section is the first air supplement inlet, and one end of the inclined section far from the vertical section is the first air injection port.

[0015] In some embodiments, there are at least two air supplement opening and closing valve plates, and at least two air supplement opening and closing valve plates are stacked along the depth direction of the valve groove.

[0016] The present invention also provides a compressor, including the above-mentioned pump body assembly.

[0017] The present invention also provides an air-conditioning refrigeration system, including the above-mentioned compressor.

[0018] A pump body assembly, a compressor, and an air-conditioning refrigeration system provided by the present invention have the following beneficial effects:

[0019] By mirror-symmetrically arranging the first air supplement inlet and the second air supplement inlet on the opposite sides of the geometric center of the air supplement opening and closing valve plate, when the air supplement opening and closing valve plate is in the air supplement position under the pressure difference at its two ends, the refrigerant gas flow at the air supplement port can flow evenly from the symmetric two-end regions of the air supplement opening and closing valve plate to achieve air supplement. In this way, it can ensure the balanced force support of the air supplement air flow on the end face of the air supplement opening and closing valve plate facing the air supplement port, and further ensure that the posture of the air supplement opening and closing valve plate is in a balanced state during the position switching process. Furthermore, it effectively reduces the generation of eccentric wear phenomenon during the opening and closing process of the air supplement opening and closing valve plate, the valve plate position switching is more stable and reliable, reduces the impact noise during the valve plate position switching process, improves the reliability of the valve plate opening and closing. At the same time, because there are two air injection channels at the same time, compared with the prior art, the jet flow rate (i.e., the air supplement flow rate) is significantly increased, and at the same time, the flow resistance of the air supplement air flow can be reduced, and the operating efficiency of the pump body assembly and the compressor is improved;

[0020] By arranging a larger-sized annular groove at the notch of the valve groove, when the air supplement opening and closing valve plate is switched from the back pressure position to the air supplement position under the pressure difference, the air supplement refrigerant has a larger flow-through area, which can ensure a larger air supplement flow rate. More importantly, at this time, there is no need to set corresponding flow holes on the air supplement opening and closing valve plate, so that the overall mass distribution of the valve plate is more balanced. In this way, it can further reduce the smooth reliability of the air supplement opening and closing valve plate during the position switching process and reduce the probability of its eccentric wear;

[0021] When 0.5 ≤ K ≤ 2.5, the compressor energy efficiency is at a relatively high level while the reliability risk is at a relatively low risk;

[0022] The first air injection channel and the second air injection channel are mirror - symmetrically arranged with respect to the central symmetry plane of the back - pressure channel, which can ensure that the frictional losses of the supplementary refrigerant in the two air injection channels are the same. Furthermore, it ensures that the supplementary air pressures entering the compression chamber are equal, which is beneficial to the stable operation of the pump body assembly;

[0023] The ejection paths of the supplementary refrigerant of the first air injection port and the second air injection port are both in a diameter direction of the cylinder, so that the injected medium - pressure gas will not cause tangential disturbance to the air flow in the cylinder. In this way, the probability of the occurrence of turbulence in the refrigerant air flow in the compression chamber can be reduced, and the vibration influence of the injected medium - pressure air flow on the compressor can be reduced;

[0024] By setting up a valve combination composed of at least two valve plates stacked together, during the impact process, part of the impact energy can be offset between at least two valve plates, reducing the impact force and preventing the valve plates from damaging the sealing member and the cylinder. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following will briefly introduce the drawings required for use in the description of the embodiments or the prior art. The drawings in the following description are only exemplary. For those of ordinary skill in the art, without creative efforts, other implementation drawings can also be obtained according to the provided drawings.

[0026] Figure 1 is the axial projection view of a cylinder using a jet valve group as a supplementary - enthalpy - increasing structure in the prior art (Prior Art 1);

[0027] Figure 2 is the axial projection view of a middle partition plate using the rotation of a roller to control the opening and closing of an air injection port to achieve air supplement in the prior art (Prior Art 2);

[0028] Figure 3 is the schematic internal structure diagram of the pump body assembly in the first embodiment of the present invention;

[0029] Figure 4 is Figure 3 the partial enlarged view at A in

[0030] Figure 5 is Figure 3 the bottom view of the cylinder in

[0031] Figure 6 is Figure 5 the sectional view taken along A - A in

[0032] Figure 7 is the schematic internal structure diagram of the pump body assembly in the second embodiment of the present invention;

[0033] Figure 8It is a schematic diagram (partial) of the internal structure of the pump body assembly in the third embodiment of the present invention;

[0034] Figure 9 It is a schematic diagram (partial) of the internal structure of the pump body assembly in the fourth embodiment of the present invention;

[0035] Figure 10 It is a schematic diagram showing the trend of the jet flow rate (i.e., the air supplement flow rate) following the crankshaft rotation angle in the first embodiment of the present invention, prior art 1, and prior art 2;

[0036] Figure 11 It is a schematic diagram of the correlation curve between S / V and energy efficiency and reliability risk in the first embodiment of the present invention;

[0037] Figure 12 It is a schematic diagram of the internal structure of the compressor in the embodiment of the present invention;

[0038] Figure 13 It is a schematic diagram of the principle of the air-conditioning refrigeration system in the embodiment of the present invention;

[0039] Figure 14 It is a schematic diagram of the jetting process of the pump body assembly in the embodiment of the present invention. In the figure, (a) is the state when the cylinder compression chamber starts jetting, (b) is the state when the cylinder compression chamber finishes jetting, and (c) is the state when the cylinder compression chamber starts exhausting;

[0040] Figure 15 It is a simulation diagram of the force condition of the air supplement opening and closing valve plate in the first embodiment of the present invention.

[0041] Reference numerals are as follows:

[0042] 1. Cylinder; 11. Back pressure channel; 121. First jet channel; 1211. First air supplement inlet; 1212. First jet port; 122. Second jet channel; 1221. Second air supplement inlet; 1222. Second jet port; 21. Valve groove; 211. Annular groove; 22. Air supplement opening and closing valve plate; 31. Air supplement port; 321. Upper flange; 322. Lower flange; 33. Middle partition plate; 4. Crankshaft; 41. Roller; 51. First muffler; 52. Second muffler; 100. Air supplement and enthalpy increase component; 101. Economizer; 102. Condenser; 103. Evaporator; 104. First throttling element; 105. Second throttling element; 106. Electromagnetic on-off valve; 107. Divider. Detailed implementation manners

[0043] The following will clearly and completely describe the technical solutions in the embodiments of the present invention with reference to the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part rather than all of the embodiments of the present invention. The description of at least one exemplary embodiment is actually only illustrative and in no way restricts the present invention and its application or use. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without creative efforts belong to the scope of protection of the present invention.

[0044] In the description of the present invention, it should be understood that the orientation or positional relationship indicated by orientation words such as "front, back, up, down, left, right", "lateral, vertical, perpendicular, horizontal" and "top, bottom", etc. is usually based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present invention and simplifying the description. Without contrary explanation, these orientation words do not indicate and imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation. Therefore, it should not be construed as a limitation on the protection scope of the present invention; the orientation words "inside, outside" refer to the inside and outside relative to the contour of each component itself.

[0045] For the convenience of description, spatial relative terms such as "above...", "over...", "on the upper surface of...", "above" etc. can be used here to describe the spatial positional relationship between a device or feature shown in the figure and other devices or features. It should be understood that the spatial relative terms are intended to include different orientations in use or operation in addition to the orientation described in the figure for the device. For example, if the device in the drawing is inverted, the device described as "above other devices or structures" or "over other devices or structures" will then be positioned as "below other devices or structures" or "under other devices or structures". Thus, the exemplary term "above..." can include both the orientations of "above..." and "below...". The device can also be positioned in other different ways (rotated 90° or in other orientations), and corresponding explanations should be made for the spatial relative descriptions used here.

[0046] In addition, it should be noted that the use of words such as "first", "second" etc. to limit components is only for the convenience of distinguishing the corresponding components. Without additional declaration, the above words have no special meaning. Therefore, it should not be construed as a limitation on the protection scope of the present invention.

[0047] See Figures 3 to 15As shown, according to an embodiment of the present invention, a pump body assembly is provided, which includes a cylinder 1 and a plugging member (not labeled in the figure) assembled on the first end face of the cylinder 1. The plugging member is a component that forms an end face plugging for the central hole of the cylinder 1. For example, the upper flange 321, the lower flange 322 or the middle partition 33 in the pump body assembly. A valve groove 21 is formed between the plugging member and the cylinder 1. In a specific embodiment, the valve groove 21 is formed on the first end face of the cylinder 1, so that the axial thickness of the plugging member can be reduced, and further the overall axial thickness of the pump body assembly can be reduced. A gas supplement port 31 communicating with the air outlet of the gas supplement and enthalpy increase component 100 (essentially a gas-liquid separator) of the compressor is formed on the plugging member. The gas supplement port 31 communicates with the valve groove 21. A back pressure channel 11 communicating with both the compression chamber (not labeled in the figure) of the pump body assembly and the valve groove 21 is formed in the cylinder 1. That is, the inlet of the back pressure channel 11 is in the compression chamber, and the outlet of the back pressure channel 11 is in the valve groove 21. A jet channel communicating with both the compression chamber and the valve groove 21 is also formed in the cylinder 1. A gas supplement opening and closing valve plate 22 is arranged in the valve groove 21. The gas supplement opening and closing valve plate 22 has a gas supplement position for communicating the gas supplement port 31 with the valve groove 21 and a back pressure position for cutting off the communication between the gas supplement port 31 and the valve groove 21. That is, in the gas supplement position, the gas supplement opening and closing valve plate 22 does not block the gas supplement port 31, and in the back pressure position, the gas supplement opening and closing valve plate 22 blocks the gas supplement port 31. The gas supplement opening and closing valve plate 22 realizes the switching between the gas supplement position and the back pressure position under the action of the pressure difference between its two end faces (the aforementioned pressure difference is the difference between the refrigerant pressure in the back pressure channel 11 and the refrigerant pressure in the gas supplement port 31). The jet channel includes a first jet airway 121 and a second jet airway 122. The first gas supplement inlet 1211 of the first jet airway 121 and the second gas supplement inlet 1221 of the second jet airway 122 are symmetrically arranged with respect to the geometric center of the gas supplement opening and closing valve plate 22. That is, when the gas supplement opening and closing valve plate 22 is circular, the first gas supplement inlet 1211 and the second gas supplement inlet 1221 are respectively located in the relative two end regions of a diameter of the gas supplement opening and closing valve plate 22, and are the same in size and shape.

[0048] In this technical solution, the first air replenishment inlet 1211 and the second air replenishment inlet 1221 are mirror - set on the relative two sides of the geometric center of the air replenishment opening and closing valve piece 22. Thus, when the air replenishment opening and closing valve piece 22 is in the air replenishment position under the pressure difference at its two ends, the refrigerant air flow at the air replenishment port 31 can flow evenly from the symmetrical two - end regions of the air replenishment opening and closing valve piece 22 to achieve air replenishment. In this way, it can ensure the balanced force support of the air replenishment air flow on the end face of the air replenishment opening and closing valve piece 22 facing the air replenishment port 31. Furthermore, it can ensure that the posture of the air replenishment opening and closing valve piece 22 is in a balanced state during the position switching process. Moreover, it effectively reduces the generation of eccentric wear phenomenon during the opening and closing process of the air replenishment opening and closing valve piece 22. The valve piece position switching is more stable and reliable, reduces the impact noise during the valve piece position switching process, and improves the reliability of the valve piece opening and closing. At the same time, since there are two jet air channels, compared with the prior art, the jet air flow (i.e., the air replenishment flow) is significantly increased. As shown in Fig. 10, it can also reduce the flow resistance of the air replenishment air flow and improve the operation efficiency of the pump body assembly and the compressor.

[0049] Specifically refer to Figure 15 As shown, this figure is the transient diagram of the air flow entering the cylinder compression chamber during the opening process of the aforementioned air replenishment opening and closing valve piece 22 (specifically a circular valve), which is generated by numerical simulation software. Through this figure, the pressure distribution cloud diagram of the refrigerant air flow on the valve piece can be clearly obtained, and the uniformity of the pressure distribution of this structure can be visually evaluated. In the figure, blue represents the lowest air flow pressure value, red represents the highest air flow pressure value, and the two green regions on both sides are the first jet air channel 121 and the second jet air channel 122 respectively. The two jet air channels are symmetrically arranged with respect to the back - pressure channel 11. It is green, indicating that the air flow pressure value in this region in this structure is medium - low pressure, and the pressure values on both sides are equal; the middle red region is the air replenishment port 31 with the highest pressure value; the color of the valve groove 21 region gradually changes from red to light red, indicating that the pressure is gradually decreasing and flowing to the symmetrical channels on both sides. The overall air flow of this structure is evenly distributed.

[0050] In some embodiments, an annular groove 211 is formed at the notch of the valve groove 21. The annular groove 211 surrounds the air replenishment port 31. It can be understood that when the aforementioned valve groove 21 and the annular groove 211 are concentric circular grooves, the diameter D1 of the annular groove 211 is greater than the diameter of the valve groove 21. At this time, the air replenishment opening and closing valve piece 22 and the valve groove 21 are in clearance fit. The fit dimension of the aforementioned clearance fit is such that the air replenishment opening and closing valve piece 22 can smoothly lift and slide in the valve groove 21 under the pressure difference. And at this time, correspondingly, the thickness H ( Figure 8 as shown) of the aforementioned air replenishment opening and closing valve piece 22 should not be less than the axial depth of the annular groove 211 to ensure the reliable limiting and guiding effect of the valve groove 21 on the valve piece. The axial depth of the aforementioned valve groove 21 can be approximately equal to the axial thickness of the air replenishment opening and closing valve piece 22.

[0051] In this technical solution, by providing an annular groove 211 with a larger size at the notch of the valve groove 21, when the air replenishing opening and closing valve piece 22 switches from the back pressure position to the air replenishing position under the action of the pressure difference, the air replenishing refrigerant has a larger flow-through area, which can ensure a larger air replenishing flow rate. More importantly, at this time, there is no need to provide corresponding flow holes on the air replenishing opening and closing valve piece 22, making the overall mass distribution of the valve piece more balanced. In this way, the stability and reliability of the air replenishing opening and closing valve piece 22 during the position switching process can be further reduced, and the probability of eccentric wear can be decreased.

[0052] Referring to Figure 5 and Figure 6 As shown, in some embodiments, the first air replenishing inlet 1211, the second air replenishing inlet 1221, and the valve groove 21 are all formed on the first end face, and when projected onto the bottom wall of the valve groove 21, the first air replenishing inlet 1211 and the second air replenishing inlet 1221 respectively have intersections with the annular groove 211.

[0053] In this technical solution, since the projections of the first air replenishing inlet 1211 and the second air replenishing inlet 1221 on the bottom wall of the valve groove 21 have intersections with the annular groove 211, the air replenishing refrigerant entering from the air replenishing port 31 can be evenly distributed to the two air replenishing inlets via the annular groove 211 and further replenished into the compression chamber, making the air flow more smooth. At the same time, since each structure is formed on the first end face of the cylinder 1, the processing is more convenient.

[0054] In a specific embodiment, the air replenishing opening and closing valve piece 22 is a circular valve piece, the valve groove 21 and the annular groove 211 are concentric circular grooves, and the channel outlet of the back pressure channel 11 is also concentric with the valve groove 21, simplifying the processing process of the components.

[0055] Define the flow-through area of the annular groove 211 as S, S = πD1 * H, where D1 is the outer diameter of the annular groove 211, with the unit of mm, H is the axial groove depth of the annular groove, with the unit of mm, and the suction volume of the corresponding cylinder 1 is V, with the unit of cm 3, define \(K = S / V\) (it should be noted that when specifically obtaining this ratio, only \(S\) and \(V\) need to be replaced with corresponding units and then the corresponding values are taken, so that \(K\) is objectively a dimensionless value), where \(0.3\leq K\leq3\), and the preferred range is \(0.5\leq K\leq2.5\). The annular groove 211 is the main path through which the jet-enhanced enthalpy refrigerant gas flows, and it is connected to the cylinder (compression chamber). If \(S\) increases, the parameters \(D1\) and \(H\) increase, the clearance volume of the cylinder increases, and the energy efficiency of the compressor will accumulate and decrease after reaching the optimal value. Its size has an important impact on the capacity of the compressor. The \(H\) parameter in the flow area of the annular groove 211 has an important impact on the inclination of the air replenishment opening and closing valve plate 22 during the position switching process. When the axial height \(A\) of the air replenishment opening and closing valve plate 22 and the axial groove depth \(B\) of the valve groove 21 are fixed, an increase in \(H\) will cause the height of the air replenishment opening and closing valve plate 22 assembled in the valve groove 21 to decrease, that is, the sliding fit (clearance fit) length between the air replenishment opening and closing valve plate 22 and the valve groove 21 decreases, which is not conducive to the reliability of the position switching of the air replenishment opening and closing valve plate 22. In the present invention, limiting \(K = S / V\) to the aforementioned range can take into account both the high operating energy efficiency of the compressor and the high reliability of air replenishment and enthalpy increase. Specifically, see Figure 11 As shown, when \(0.5\leq K\leq2.5\), the energy efficiency of the compressor is at a relatively high level while the reliability risk is at a relatively low level.

[0056] Specifically, see Figure 5 As shown, in some embodiments, the first air injection channel 121 and the second air injection channel 122 are mirror-symmetrically arranged with respect to the central symmetry plane of the back pressure channel 11. Specifically, in the axial projection of the cylinder 1 (that is, in the radial plane of the cylinder 1 along the axial projection), the connection line between the projection of the center line of the back pressure channel 11 and the center point of the cylinder is the first line. At this time, the first air injection channel 121 and the second air injection channel 122 are symmetric about this first line on the left and right.

[0057] In this technical solution, the first air injection channel 121 and the second air injection channel 122 are mirror-symmetrically arranged with respect to the central symmetry plane of the back pressure channel 11, which can ensure that the frictional losses of the air replenishment refrigerant in the two air injection channels are the same, and further ensure that the air replenishment pressures entering the compression chamber are equal, which is beneficial to the stable operation of the pump body assembly.

[0058] Further see Figure 5 As shown, in some embodiments, the first air injection channel 121 has a first air injection port 1212 on the inner wall of the cylinder 1 of the cylinder, and the second air injection channel 122 has a second air injection port 1222 on the inner wall of the cylinder 1 of the cylinder. In the projection on any radial plane of the pump body assembly, the center line of the air injection path of the first air injection port 1212 and / or the second air injection port 1222 passes through the center point of the cylinder 1, that is, the air injection paths of the air replenishment refrigerant of the first air injection port 1212 and the second air injection port 1222 are both in a diameter direction of the cylinder 1.

[0059] In this technical solution, the injection paths of the supplementary refrigerant of the first injection port 1212 and the second injection port 1222 are both in a diameter direction of the cylinder 1, so that the medium-pressure gas replenished will not cause tangential disturbance to the air flow in the cylinder 1. In this way, the probability of the occurrence of the turbulence phenomenon of the refrigerant air flow in the compression chamber can be reduced, and the vibration influence of the replenished medium-pressure air flow on the compressor can be reduced.

[0060] In some embodiments, the first air injection channel 121 has a vertical section (not labeled in the figure) extending along the axial direction of the cylinder 1 and an inclined section (not labeled in the figure) extending obliquely along the side close to the compression chamber. The vertical section is communicated with the inclined section, and one end of the vertical section far from the inclined section is the first air replenishment inlet 1211, and one end of the inclined section far from the vertical section is the first injection port 1212, so as to facilitate the machining of the first air injection channel 121 and the second air injection channel 122 by a tool. In a preferred embodiment, the included angle between the inclined section and the vertical section is an obtuse angle, so as to reduce the frictional resistance along the flow of the supplementary refrigerant therein.

[0061] In Figure 9 In a specific embodiment shown, there are at least two air replenishment opening and closing valve plates 22. At least two air replenishment opening and closing valve plates 22 are stacked along the depth direction of the valve groove 21. At this time, it can be understood that the axial thickness of each air replenishment opening and closing valve plate 22 cannot be less than the axial depth of the annular groove 211 to ensure that each air replenishment opening and closing valve plate 22 can slide reliably in the valve groove 21. As described above, the air replenishment opening and closing valve plate 22 performs opening and closing movements through the pressure difference at both ends thereof. During the opening and closing of the air injection, the air replenishment opening and closing valve plate 22 is an impact object, and the aforementioned sealing member (the middle partition plate 33 or the upper flange 321 or the lower flange 322) and the cylinder 1 are the impacted objects. Under the test conditions of high-frequency and high-pressure ratio, the pressure in the compression chamber changes rapidly, its pressure ratio is large, and the impact force of the valve plate opening and closing action on the sealing member and the valve groove 21 on the cylinder 1 is large. The sealing member and the cylinder 1 have a high risk of cracking. By setting a valve combination composed of at least two stacked valve plates, during the impact process, part of the impact energy can be offset between at least two valve plates, reducing the impact force and reducing the impact damage of the valve plate on the sealing member and the cylinder 1.

[0062] Figure 8 and Figure 9Another embodiment of the present invention is shown. Specifically, the pump body assembly is a double-cylinder pump body assembly. At this time, the air supplement port 31 is formed on the middle partition plate 33, and the valve grooves 21 are respectively formed on the end faces of the upper and lower cylinders cooperating with the middle partition plate 33 (i.e., the aforementioned first end face). The aforementioned air supplement opening and closing valve plates 22 are respectively arranged in the valve grooves 21, thereby realizing medium-pressure air supplement to the compression chambers in each cylinder of the pump body assembly.

[0063] It can be understood that the pump body assembly further includes a first silencer 51 and a second silencer 52. A roller 41 is arranged in the cylinder 1, and the roller 41 is sleeved on the eccentric part of the crankshaft 4.

[0064] According to an embodiment of the present invention, specifically refer to Figure 12 As shown, a compressor is further provided, which can specifically be called an ejector-enhanced enthalpy compressor or an ejector compressor. It includes the above-mentioned pump body assembly. The pump body assembly is arranged in the compressor housing. A liquid distributor 107 communicating with the suction port of the pump body assembly and an ejector-enhanced enthalpy component 100 communicating with the air supplement port 31 are connected to the compressor housing.

[0065] As Figure 12As shown, the jet enthalpy-increasing compressor is composed of a liquid separator component, a jet liquid separator component, a housing assembly, the aforementioned pump body assembly, and a motor assembly. The pump body assembly and the motor assembly are arranged inside the housing assembly, and the motor assembly is arranged above the pump body assembly; the motor assembly is connected to the crankshaft of the pump body assembly; the motor assembly includes a rotor and a stator. The rotor rotates under the action of magnetic pulling force, and the crankshaft transmits the rotational force generated by the rotor to the pump body assembly; the stator is wound with multiple coils, and magnetic force can be generated by energizing it; the stator is connected to a sealed terminal outside its housing and is energized through the terminal; the rotor has a conductor made of materials such as neodymium iron boron or aluminum rod and rotates under the action of the magnetic force generated by the energized coil of the stator; the rotational torque transmitted by the crankshaft to the pump body assembly compresses the low-pressure gaseous refrigerant sucked into the pump body assembly and discharges the high-pressure gaseous refrigerant out of the housing assembly; after compression, the inner cavity of the housing assembly is filled with high-temperature and high-pressure gaseous refrigerant; in addition, lubricating oil for lubricating and dissipating heat from the pump body assembly is stored in the lower part of the housing assembly; the crankshaft (i.e., the aforementioned crankshaft 4) is arranged in series between the first muffler (i.e., the aforementioned first muffler 51), the first flange (i.e., the aforementioned upper flange 321), the first cylinder (i.e., the upper cylinder 1), the partition plate (i.e., the aforementioned middle partition plate 33), the second cylinder (i.e., the lower cylinder 1), the second flange (i.e., the aforementioned lower flange 322), and the second muffler (i.e., the aforementioned second muffler 52); the roller (i.e., the aforementioned roller 41) is assembled on the eccentric part of the crankshaft, and the sliding vane is assembled in the sliding vane groove of the cylinder to form the pump body assembly; with the center axis of the crankshaft as the rotation center, the roller is driven to rotate inside the pump body assembly to compress the gaseous refrigerant; the liquid separator component and the housing assembly are fixed by welding with a bracket, the suction end is connected to the refrigerant from the evaporator, and the discharge end is connected to the suction port of the pump body assembly; the jet liquid separator component and the housing assembly are fixed by welding with a bracket, the suction end is connected to the medium-pressure gaseous refrigerant from the economizer, and the discharge end is connected to the jet channel of the partition plate; the jet enthalpy-increasing compressor sucks the refrigerant from the evaporator and completes a working cycle through compression, jetting, and exhaust.

[0066] According to an embodiment of the present invention, specifically refer to Figure 13As shown in the figure, an air-conditioning refrigeration system is further provided, including the above-mentioned compressor. Specifically, the exhaust port of the compressor is communicated with the inlet of the condenser 102, and the outlet of the condenser 102 is sequentially communicated with the first inlet of the economizer 101 via the electromagnetic on-off valve 106 and the first throttling element 104 (specifically, it can be an electronic expansion valve). At the same time, the outlet of the condenser 102 is also communicated with the second inlet of the economizer 101. The liquid outlet of the economizer 101 is communicated with the inlet of the evaporator 103 via the second throttling element 105, and the outlet of the evaporator 103 is communicated with the suction port of the compressor pump body assembly via the liquid distributor 107. The gas outlet of the aforesaid economizer 101 is communicated with the gas injection port 31 via the aforesaid gas injection and enthalpy-increasing component 100. In this technical solution, when the electromagnetic on-off valve 106 is closed, the air-conditioning refrigeration system is a single-stage compression refrigeration system, and the refrigerant completes a refrigeration cycle through the compressor, the condenser 102, the economizer 101, the second throttling element 105, and the evaporator 103. When the electromagnetic on-off valve 106 is opened, the air-conditioning refrigeration system is a jet injection and enthalpy-increasing refrigeration system. The refrigerant flowing out of the condenser 102 is divided into a jet injection circuit and a main circuit. In the jet injection circuit, the refrigerant is throttled by the first throttling element 104 and then enters the economizer 101 for heat exchange and enters the jet injection channel of the compressor. In the main circuit, the refrigerant is subcooled in the economizer 101 and then throttled by the second throttling element 105 and enters the evaporator 103. After the refrigerant flows out of the evaporator 103, it is sucked into the compressor through the suction port, completing a refrigeration cycle.

[0067] As Figure 13 shown, the jet liquid distributor component (i.e., the aforesaid gas injection and enthalpy-increasing component 100) sucks in the medium-pressure gaseous refrigerant from the economizer 101, which is called the jet injection medium pressure Pm; the pressure of the cylinder compression chamber is Pd; when the compression chamber pressure Pd is less than Pm, the valve plate is lifted to the gas injection position, that is, it is in the open state, as Figure 8 shown by the state of the upper valve plate in the figure; when the compression chamber pressure Pd is greater than Pm, the valve plate is closed under the action of the gas pressure difference, that is, the valve plate is in the back pressure position, as Figure 8The state of the valve plate at the lower part. The jet path is as follows: The medium-pressure jet enters the compressor pump body from the jet inlet through the jet distributor component, and enters the valve plates of the upper and lower cylinders respectively through the enthalpy-increasing port of the middle partition plate (i.e., the aforementioned air supplement port 31). In the first stage of the jet compressor, after the roller passes the suction port, compression starts in the cylinder compression chamber. The initial pressure in the cylinder compression chamber is low pressure. During the initial compression process, the jet pressure Pm is higher than the pressure Pd in the cylinder compression chamber. Under the action of the gas pressure difference, the circular valve opens, and the medium-pressure jet airflow enters the cylinder compression chamber through the jet channel on the cylinder to achieve jetting. As the compression process progresses, it enters the second stage of the jet compressor. The pressure Pd in the cylinder compression chamber gradually increases. When the pressure in the cylinder compression chamber is higher than the jet pressure Pm, the circular valve closes under the action of the gas pressure difference, completing the jetting and closing the enthalpy-increasing port. Finally, it reaches the third stage of exhaust in the cylinder compression chamber jetting, completing the jetting cycle process, as Figure 14 shown.

[0068] Continue to refer to Figure 14 , the compression of the jet compressor can be divided into three stages. First, after the suction ends, the first compression stage begins. In this stage, the pressure in the compression chamber is lower than the jet pressure, creating a pressure difference inside and outside. The jet valve plate opens, and the gaseous refrigerant jets into the cylinder compression chamber through the jet path (as Figure 14 a); Second, as the volume of the cylinder compression chamber becomes smaller, the air pressure in the cylinder compression chamber gradually increases. When the pressure in the cylinder compression chamber is greater than the pressure at the jet port, the jet valve plate closes, and the jetting process ends (as Figure 14 b); Third, after the pressure in the cylinder compression chamber further increases to the exhaust pressure, until the compressor exhausts, the compression process ends (as Figure 14 c).

[0069] It is easy for those skilled in the art to understand that, on the premise of no conflict, the advantageous technical features of the above various methods can be freely combined and superimposed.

[0070] The above are only the preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent replacements, and improvements made within the spirit and principle of the present invention shall be included within the protection scope of the present invention. The above is only the preferred implementation manner of the present invention. It should be noted that for those of ordinary skill in the art in this technical field, without departing from the technical principle of the present invention, several improvements and variations can still be made, and these improvements and variations should also be regarded as within the protection scope of the present invention.

Claims

1. A pump assembly, comprising a cylinder (1) and a plugging member assembled on a first end surface of the cylinder (1), a valve groove (21) being constructed between the plugging member and the cylinder (1), a gas replenishment port (31) being constructed on the plugging member, the gas replenishment port (31) being communicated with the valve groove (21), a back pressure channel (11) being constructed in the cylinder (1) and being communicated with both a compression chamber of the pump assembly and the valve groove (21), and a back pressure channel (11) being constructed in the cylinder (1) and being communicated with the compression chamber of the pump assembly and the valve groove (21). The air supply opening and closing valve plate (22) is provided in the valve groove (21), and the air supply opening and closing valve plate (22) has an air supply position for connecting the air supply port (31) with the valve groove (21) and a back pressure position for cutting off the connection between the air supply port (31) and the valve groove (21). The air supply opening and closing valve plate (22) can switch between the air supply position and the back pressure position under the pressure difference between the two end surfaces thereof, and is characterized in that: The jet channel comprises a first jet channel (121) and a second jet channel (122); a first air supply inlet (1211) of the first jet channel (121) and a second air supply inlet (1221) of the second jet channel (122) are arranged in a mirror image with respect to the geometric center of the air supply opening and closing valve plate (22).

2. The pump assembly according to claim 1, characterized in that: An annular groove (211) is formed at the notch of the valve groove (21), the annular groove (211) is arranged around the air supply port (31), and a clearance fit is formed between the air supply opening and closing valve plate (22) and the valve groove (21).

3. The pump assembly according to claim 2, characterized in that: The first air supply inlet (1211) and the second air supply inlet (1221) are both constructed on the first end surface and projected onto the bottom wall of the valve groove (21); the first air supply inlet (1211) and the second air supply inlet (1221) respectively have an intersection with the annular groove (211); and / or the air supply opening and closing valve plate (22) is a circular valve plate, and the valve groove (21) and the annular groove (211) are concentrically arranged circular grooves.

4. The pump assembly according to claim 2, characterized in that: The suction volume of the pump body assembly is V, the flow area of ​​the annular groove (211) is S, and 0.3≤S / V≤3.

5. The pump assembly according to claim 1, characterized in that: The first jet passage (121) and the second jet passage (122) are arranged in a mirror-like manner with respect to a central symmetry plane of the back-pressure passage (11).

6. The pump assembly according to claim 1, characterized in that: The first jet passage (121) has a first jet port (1212) located on the inner wall of the cylinder (1), and the second jet passage (122) has a second jet port (1222) located on the inner wall of the cylinder (1). When projected onto any radial surface of the pump body assembly, a center line of the jet path of the first jet port (1212) and / or the second jet port (1222) passes through the center point of the cylinder (1).

7. The pump assembly according to claim 6, characterized in that: The first jet channel (121) comprises a vertical section extending along the axial direction of the cylinder (1) and an inclined section extending obliquely along a side close to the compression chamber, the vertical section is connected to the inclined section, and the end of the vertical section away from the inclined section is the first air supplement inlet (1211), and the end of the inclined section away from the vertical section is the first jet port (1212).

8. The pump assembly according to claim 1, characterized in that: There are at least two of the air-supplying on-off valve plates (22), and the at least two air-supplying on-off valve plates (22) are stacked along the depth direction of the valve slot (21).

9. A compressor, characterized in that: A pump body assembly comprising any one of claims 1 to 8.

10. An air conditioning refrigeration system, characterized in that: Comprising the compressor as claimed in claim 9.

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