Compressor and heat pump system

Abstract

The utility model discloses a compressor and heat pump system relates to compressor technical field, compressor includes shell, pump body subassembly and motor subassembly, pump body subassembly includes cylinder, roller, slip sheet and crankshaft, cylinder is equipped with the compression chamber and slip sheet groove that are communicated, roller is rotatingly provided in the compression chamber, slip sheet is slidingly provided in slip sheet groove, and the crankshaft is equipped with the motor subassembly. One end of the sliding piece abuts against the peripheral wall of the roller or is connected with the roller, and the compression cavity is divided into an air suction cavity and an exhaust cavity through the sliding piece. The air cylinder is provided with a first air supplementing channel, a second air supplementing channel is arranged on the side, facing the exhaust cavity, of the sliding piece, one end of the first air supplementing channel penetrates through the peripheral wall of the air cylinder, in the moving process of the sliding piece, the other end of the first air supplementing channel is communicated with the second air supplementing channel, and the second air supplementing channel is intermittently communicated with the exhaust cavity. The air supply channel of the compressor is simple in structure, easy to machine, beneficial to reducing machining cost, large in air supply amount and capable of enhancing the heating effect at the low temperature.

Description

Technical Field

[0001] This utility model relates to the field of compressor technology, and in particular to a compressor and heat pump system. Background Technology

[0002] In cold and extremely cold climates, conventional heat pump air conditioners have poor low-temperature heating performance, making it difficult to meet residents' heating needs. To improve the heating performance of heat pump air conditioners in cold environments, an enthalpy-enhancing jet structure is added to the compressor. This structure introduces a portion of the refrigerant from the high-pressure side condenser into the compressor's compression chamber, thereby enhancing the heating effect at low temperatures.

[0003] Existing enthalpy-enhancing injection methods generally use valve-type nozzles to inject gas into the compression chamber. However, this type of enthalpy-enhancing injection method has a complex structure and high manufacturing cost. Some enthalpy-enhancing injection structures are located in rollers, resulting in a small injection volume, which is difficult to meet the heating requirements of the compressor at low temperatures. Utility Model Content

[0004] This invention aims to solve at least one of the technical problems existing in the prior art. To this end, this invention proposes a compressor with a simple air supply channel structure that is easy to manufacture, which helps to reduce manufacturing costs, and has a large air supply capacity to enhance the heating effect at low temperatures.

[0005] This utility model also provides a heat pump system having the above-mentioned compressor.

[0006] A compressor according to a first aspect of the present invention includes a housing; a pump assembly disposed within the housing, the pump assembly including a cylinder, a roller, a vane, and a crankshaft, the cylinder having a communicating compression chamber and a vane groove, the roller being rotatably disposed in the compression chamber, the vane being slidably disposed in the vane groove, one end of the vane abutting against the outer peripheral wall of the roller or connected to the roller, and the vane dividing the compression chamber into an intake chamber and an exhaust chamber, one end of the crankshaft having an eccentric portion connected to the roller; a motor assembly including a stator and a rotor, the rotor being rotatably disposed in the inner hole of the stator, and the rotor being connected to the other end of the crankshaft; wherein, the cylinder has a first air supply channel, the vane having a second air supply channel on the side facing the exhaust chamber, one end of the first air supply channel penetrating the outer peripheral wall of the cylinder, and during the movement of the vane, the other end of the first air supply channel maintaining communication with the second air supply channel, the second air supply channel being intermittently communicating with the exhaust chamber.

[0007] The compressor according to the first aspect of this utility model has at least the following beneficial effects: By providing a first air supply channel in the cylinder and a second air supply channel communicating with the first air supply channel in the sliding vane, the structures of the first and second air supply channels are relatively simple and easy to process separately, which helps to reduce processing costs. During compressor operation, when the sliding vane moves to communicate with the exhaust chamber through the second air supply channel, part of the refrigerant in the high-pressure side condenser is supplied to the exhaust chamber through the first and second air supply channels, thereby reducing the compressor's exhaust temperature and increasing the exhaust volume, thus enhancing the heating effect in low-temperature environments. Simultaneously, the air supply volume can be increased by increasing the cross-sectional area of ​​the first and second air supply channels, which further enhances the heating effect in low-temperature environments. Furthermore, since the first and second air supply channels remain connected, the force on the sliding vane in the thickness direction is more stable, reducing fluctuations and thus improving reliability.

[0008] According to some embodiments of the present invention, the first air supply channel includes a first channel, a second channel, and a third channel connected in sequence. The first channel is arranged radially along the cylinder and penetrates the outer peripheral wall of the cylinder. The second channel is arranged axially along the cylinder. The third channel is located on the axial end face of the cylinder and is connected to the second air supply channel.

[0009] According to some embodiments of the present invention, the cross-sectional area of ​​the first channel is S1, and the cross-sectional area of ​​the third channel is S3, satisfying: 1≤S1 / S3≤3.

[0010] According to some embodiments of the present invention, the minimum cross-sectional area of ​​the second channel is S2, and the cross-sectional area of ​​the third channel is S3, satisfying: 1≤S2 / S3≤3.

[0011] According to some embodiments of the present invention, the cross-sectional area of ​​the second air supply channel is S4, and the cross-sectional area of ​​the third channel is S3, satisfying: 1≤S3 / S4≤2.

[0012] According to some embodiments of the present invention, the cylinder is further provided with an air intake hole communicating with the air intake chamber, and the angle between the central axis of the air intake hole and the central axis of the first channel is θ, satisfying: 20°≤θ≤110°.

[0013] According to some embodiments of the present invention, the second channel includes a tapered section that connects to the third channel. One end of the tapered section penetrates the axial end face of the cylinder, and the inner diameter of the tapered section decreases from the third channel to the first channel along the axial direction of the cylinder. A tapered pin is installed in the tapered section, and the tapered pin is configured to make the second channel and the third channel either connected or blocked.

[0014] According to some embodiments of this utility model, the second air supply channel is located between two end faces of the sliding vane that are opposite to each other along the axial direction of the cylinder; or,

[0015] The second air supply channel passes through one of the two end faces of the slide.

[0016] According to some embodiments of the present invention, along the sliding direction of the slide, the distance between the end of the second air supply channel facing the compression chamber and the end of the slide facing the roller is L1, which satisfies: 2mm≤L1≤10mm.

[0017] According to some embodiments of the present invention, along the sliding direction of the slide, the length of the second air supply channel is L2, and the length of the slide is L3, satisfying: 2mm≤L2≤L3-L1-2.

[0018] According to some embodiments of the present invention, the thickness of the sliding plate is T, and the depth of the second air supply channel along the thickness direction of the sliding plate is H, satisfying: 1mm≤H≤T / 2.

[0019] According to some embodiments of this utility model, the cross-section of the second air supply channel is S4, which satisfies: 1mm 2 ≤S4≤25mm 2 .

[0020] The heat pump system according to a second aspect of the present invention includes the compressor of the first aspect of the present invention.

[0021] The heat pump system according to the second aspect of this utility model has at least the following beneficial effects: Since the heat pump system uses the aforementioned compressor, by providing a first air supply channel in the cylinder and a second air supply channel communicating with the first air supply channel in the sliding vane, the structures of the first and second air supply channels are relatively simple and easy to process separately, which helps reduce processing costs. During compressor operation, when the sliding vane moves to connect the second air supply channel with the exhaust chamber, part of the refrigerant in the high-pressure side condenser is supplied to the exhaust chamber through the first and second air supply channels, thereby reducing the compressor's exhaust temperature and increasing the exhaust volume, thus enhancing the heating effect in low-temperature environments. Simultaneously, the air supply volume can be increased by increasing the cross-sectional area of ​​the first and second air supply channels, which further enhances the heating effect in low-temperature environments. Furthermore, since the first and second air supply channels remain connected, the force on the sliding vane in the thickness direction is more stable, reducing fluctuations and thus improving reliability.

[0022] Additional aspects and advantages of this invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0023] The present invention will be further described below with reference to the accompanying drawings and embodiments, wherein:

[0024] Figure 1 This is a cross-sectional view of the compressor in an embodiment of this utility model;

[0025] Figure 2 This is a partial cross-sectional view of the compressor from another perspective in an embodiment of this utility model.

[0026] Figure 3 This is a cross-sectional schematic diagram of the cylinder and roller assembly in an embodiment of this utility model;

[0027] Figure 4 This is an axial schematic diagram of the cylinder and roller engagement when the second air supply channel and the exhaust chamber are blocked in an embodiment of this utility model.

[0028] Figure 5 This is an axial schematic diagram of the cylinder and roller engagement when the second air supply channel and the exhaust chamber are connected in an embodiment of this utility model.

[0029] Figure 6 This is a front view of the slider in an embodiment of this utility model;

[0030] Figure 7 This is a top view of the slider in an embodiment of this utility model;

[0031] Figure 8 This is a schematic diagram of the heat pump system in an embodiment of this utility model;

[0032] Figure 9 This is a partial cross-sectional view of the cylinder and roller engaging when the second and third channels are blocked in another embodiment of this utility model;

[0033] Figure 10 This is a partial cross-sectional view of the cylinder and roller engaging when the second and third channels are connected in another embodiment of this utility model.

[0034] Figure label:

[0035] Compressor 1000; First liquid receiver 1100; First refrigerant pipe 1110; Air inlet 1120; Second liquid receiver 1200; Second refrigerant pipe 1210; Condenser 1300; First throttle valve 1400; Evaporator 1500; Second throttle valve 1600;

[0036] Casing 100; Exhaust port 110;

[0037] Pump body assembly 200; cylinder 210; compression chamber 211; intake chamber 2111; exhaust chamber 2112; vane groove 212; intake port 213; exhaust port 214; roller 220; vane 230; crankshaft 240; eccentric part 241; first air supply channel 250; first channel 251; second channel 252; conical section 2521; conical pin 2522; third channel 253; second air supply channel 260; first bearing 270; second bearing 280; partition plate 290;

[0038] Motor assembly 300; stator 310; rotor 320. Detailed Implementation

[0039] The embodiments of this utility model are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this utility model, and should not be construed as limiting this utility model.

[0040] In the description of this utility model, it should be understood that the directional descriptions, such as up, down, front, back, left, right, etc., indicate the directional or positional relationship based on the directional or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.

[0041] In the description of this utility model, "several" means one or more, "multiple" means two or more, "greater than," "less than," and "exceeding" are understood to exclude the stated number, while "above," "below," and "within" are understood to include the stated number. If "first" or "second" is used in the description, it is only for the purpose of distinguishing technical features and should not be construed as indicating or implying relative importance, or implicitly indicating the number of indicated technical features, or implicitly indicating the order of the indicated technical features.

[0042] In the description of this utility model, unless otherwise explicitly defined, terms such as setting, installing, connecting, assembling, and cooperating should be interpreted broadly, and those skilled in the art can reasonably determine the specific meaning of the above terms in this utility model in conjunction with the specific content of the technical solution.

[0043] In low-temperature environments, such as cold or extremely cold climates, the heating performance of conventional heat pump air conditioners is poor, making it difficult to meet the heating needs of residents. To address this, related technologies incorporate an enthalpy-enhancing jet structure into the compressor of the heat pump air conditioner. This structure can be a valve-type jet port located in the cylinder and connected to the compression chamber, or a make-up air port located on the roller and connected to the compression chamber. This allows some of the refrigerant from the high-pressure side condenser to be introduced into the compression chamber via the enthalpy-enhancing jet structure, increasing the exhaust volume and thus improving the heating performance of the heat pump air conditioner in low-temperature environments.

[0044] However, among the aforementioned enthalpy-increasing jet structures, the valve plate type jet port has a relatively complex structure and high processing cost; and due to the limitations of the roller structure, the amount of air supplied by the air supply port on the roller is small, making it difficult to meet the heating requirements of the compression chamber in low-temperature environments.

[0045] Therefore, referring to Figures 1 to 10 As shown, the first aspect of this utility model provides a compressor 1000, which is applied to a heat pump system, such as a heat pump air conditioner or a heat pump water heater.

[0046] The following section uses a heat pump air conditioner as an example to explain in detail the specific structural composition of the compressor 1000 in a heat pump air conditioner.

[0047] Reference Figure 1 and Figure 2 As shown, the compressor 1000 includes a housing 100, a pump assembly 200, and a motor assembly 300. The compressor 1000 also includes a first liquid receiver 1100, a first refrigerant pipe 1110 connecting the first liquid receiver 1100 and the housing 100, a second liquid receiver 1200, and a second refrigerant pipe 1210 connecting the second liquid receiver 1200 and the housing 100. Specifically, the housing 100 is generally cylindrical in shape and has an inner cavity. The pump assembly 200 and the motor assembly 300 are both installed within the inner cavity of the housing 100. The first liquid receiver 1100 and the second liquid receiver 1200 are both located radially outward from the housing 100. The housing 100 can be arranged horizontally or vertically.

[0048] It is easy to understand that if the casing 100 is arranged vertically, then the compressor 1000 is a vertical compressor. If the casing 100 is arranged horizontally, then the compressor 1000 is a horizontal compressor.

[0049] It is easy to understand that different layouts of the compressor 1000 can be selected based on the layout space of the compressor 1000 in the heat pump air conditioner, thereby improving applicability.

[0050] Reference Figure 1As shown, it can be understood that in this embodiment, the compressor 1000 is a vertical compressor, and the motor assembly 300 is located above the pump body assembly 200.

[0051] Reference Figure 1 As shown, the pump assembly 200 can be a single-cylinder, double-cylinder, or multi-cylinder structure. Specifically, the pump assembly 200 includes a cylinder 210, rollers 220, vanes 230, and a crankshaft 240. The number of cylinders 210 differs between single-cylinder, double-cylinder, and multi-cylinder pump assemblies 200. When there are two or more cylinders 210, they are arranged sequentially in a vertical direction. It is easy to understand that the number of rollers 220 and vanes 230 is equal to the number of cylinders 210. The single-cylinder, double-cylinder, or multi-cylinder pump assemblies 200 correspond to compressors 1000 with different displacements.

[0052] Reference Figure 1 and Figure 3 As shown, in this embodiment, the pump body assembly 200 has a dual-cylinder structure, with two cylinders 210 arranged sequentially in the vertical direction. The specific structure of the pump body assembly 200 will be described in detail using one of the cylinders 210 as an example. Specifically, the cylinder 210 is provided with a compression chamber 211 and a vane groove 212. The compression chamber 211 extends through the upper and lower end faces of the cylinder 210, and the vane groove 212 is located on the radial side of the compression chamber 211 and communicates with it. The roller 220 has a cylindrical structure and is rotatably disposed in the compression chamber 211, with the central axis of the roller 220 offset from the central axis of the compression chamber 211. The slide plate 230 is slidably mounted in the slide plate groove 212 along the radial direction of the compression chamber 211, and the end of the slide plate 230 near the roller 220 abuts against the outer peripheral wall of the roller 220, or the end of the slide plate 230 near the roller 220 is hinged to the roller 220. Thus, the slide plate 230 and the roller 220 divide the compression chamber 211 into an intake chamber 2111 and an exhaust chamber 2112, which are located on both sides of the thickness direction of the slide plate 230.

[0053] Reference Figure 3 and Figure 4 As shown, it can be understood that the cylinder 210 is also provided with an intake port 213 and an exhaust port 214, wherein the intake port 213 communicates with the intake chamber 2111, and the exhaust port 214 communicates with the exhaust chamber 2112. It is easy to understand that the first refrigerant pipe 1110 connecting the housing 100 and the first liquid reservoir 1100 communicates with the intake port 213, so that the low-pressure refrigerant in the first liquid reservoir 1100 enters the intake chamber 2111 through the intake port 213, and can then compress the refrigerant to perform work through the roller 220.

[0054] Reference Figure 1As shown, it can be understood that the pump body assembly 200 also includes a first bearing 270, a second bearing 280, and a partition 290. The partition 290 is disposed between the two cylinders 210 and covers one end of the two compression chambers 211. The first bearing 270 is located on the upper side of the upper cylinder 210 and covers the other end of the compression chamber 211. The second bearing 280 is located on the lower side of the lower cylinder 210 and covers the other end of the other compression chamber 211.

[0055] Reference Figure 1 As shown, it can be understood that the crankshaft 240 is arranged in the vertical direction, and the lower section of the crankshaft 240 is provided with an eccentric part. The number of eccentric parts 241 is equal to the number of rollers 220, and the eccentric parts 241 and rollers 220 are rotatably connected.

[0056] Reference Figure 1 As shown, it can be understood that the motor assembly 300 is located above the first bearing 270. Specifically, the motor assembly 300 includes a stator 310 and a rotor 320. The stator 310 is fixedly connected to the inner peripheral wall of the housing 100, and the rotor 320 is rotatably disposed in the inner hole of the stator 310. The upper section of the crankshaft 240 passes through the rotor 320 and is fixedly connected to the rotor 320.

[0057] Therefore, during the operation of the compressor 1000, the motor assembly 300 drives the crankshaft 240 to rotate, and the crankshaft 240 drives the roller 220 to rotate eccentrically in the compression chamber 211, thereby compressing the refrigerant in the compression chamber 211 to perform work.

[0058] Reference Figures 3 to 5 As shown, the cylinder 210 is also provided with a first air supply channel 250, and the vane 230 is provided with a second air supply channel 260. One end of the first air supply channel 250 penetrates the outer peripheral wall of the cylinder 210, and the other end penetrates the side wall of the vane groove 212. The second air supply channel 260 is located on the side of the vane 230 facing the exhaust chamber 2112, and the opening of the second air supply channel 260 faces the first air supply channel 250. Within the travel range of the vane 230, the first air supply channel 250 and the second air supply channel 260 remain in communication.

[0059] Reference Figure 4 and Figure 5As shown, it can be understood that as the roller 220 rotates, the slide 230 reciprocates within the slide groove 212, and the end of the slide 230 facing the roller 220 always abuts against or connects to the outer peripheral wall of the roller 220, causing a portion of the opening of the second air supply channel 260 on the slide 230 to be exposed in the exhaust chamber 2112, or the second air supply channel 260 to be entirely located within the slide groove 212. It is easy to understand that when a portion of the opening of the second air supply channel 260 is exposed in the exhaust chamber 2112, the second air supply channel 260 is connected to the exhaust chamber 2112; when the second air supply channel 260 is entirely located within the slide groove 212, the second air supply channel 260 is blocked from the exhaust chamber 2112. In other words, within the range of the slide 230's travel, the second air supply channel 260 is intermittently connected to the exhaust chamber 2112.

[0060] Reference Figure 1 , Figure 2 and Figure 8 The diagram shown illustrates the working principle of a heat pump air conditioner. It can be understood that the heat pump air conditioner includes a compressor 1000, a condenser 1300, a first throttling valve 1400, an evaporator 1500, and a second throttling valve 1600. An exhaust port 110 is located on the top of the housing 100, and an air inlet 1120 is located on the top of the first liquid receiver 1100. The exhaust port 110 is connected to the condenser 1300, and the air inlet 1120 is connected to the evaporator 1500. The condenser 1300 and evaporator 1500 are connected via the first throttling valve 1400. The condenser 1300 is also connected to the second liquid receiver 1200 of the compressor 1000 via the second throttling valve 1600. The second liquid receiver 1200 is connected to the first refrigerant supply channel 250 via a second refrigerant pipe 1210. During the operation of a heat pump air conditioner, the compressor 1000 compresses the refrigerant, bringing it to a high-temperature, high-pressure state. This high-temperature, high-pressure refrigerant flows to the condenser 1300, where it releases heat to heat the user's living space. After releasing heat, the refrigerant flows through the first expansion valve 1400 to the evaporator 1500. At the evaporator 1500, the refrigerant absorbs heat and evaporates into a gaseous state, flowing to the first liquid receiver 1100 of the compressor 100, and then to the compression chamber 211 of the cylinder 210. The compressor 1000 then compresses the refrigerant again, and this cycle continues to meet the user's heating needs.

[0061] Reference Figure 5 and Figure 8As shown, it can be understood that during the operation of the compressor 1000, when the vane 230 moves to the position that connects the second gas supply channel 260 with the exhaust chamber 2112, part of the refrigerant after heat exchange in the condenser 1300 flows through the second throttle valve 1600 to the second liquid receiver 1200, then through the second refrigerant pipe 1210 to the first gas supply channel 250, and then through the second gas supply channel 260 to replenish the exhaust chamber 2112. This can reduce the exhaust temperature of the compressor 1000, reduce heat loss, improve the operating efficiency of the compressor 1000, and increase the exhaust volume, thereby effectively improving the heating capacity in low-temperature environments.

[0062] It is understandable that, since the first air supply channel 250 is located in the cylinder 210 and the second air supply channel 260 is located in the slide vane 230, the first air supply channel 250 and the second air supply channel 260 can be machined separately during processing. Furthermore, the structures of the first air supply channel 250 and the second air supply channel 260 are relatively simple and easy to process, which helps to reduce processing costs.

[0063] Understandably, since the structures of the first air supply channel 250 and the second air supply channel 260 are relatively simple, their cross-sectional areas are easily adjusted according to actual conditions. Therefore, provided that the structural strength requirements of the cylinder 210 and the vane 230 are met, the air supply volume can be increased by increasing the cross-sectional areas of the first air supply channel 250 and the second air supply channel 260, thereby further enhancing the heating effect in low-temperature environments.

[0064] It is understandable that, since the first gas supply channel 250 and the second gas supply channel 260 remain connected during the operation of the compressor 1000, the force exerted by the supplemented refrigerant on the vane 230 in the thickness direction of the vane 230 is relatively stable, making the force on the vane 230 in the thickness direction more stable and with less fluctuation, which is conducive to maintaining the movement stability of the vane 230 and thus improving reliability.

[0065] Reference Figures 3 to 5As shown, the first air supply channel 250 includes a first channel 251, a second channel 252, and a third channel 253 connected in sequence. Specifically, the first channel 251 is arranged radially along the cylinder 210, extending from the outer peripheral wall of the cylinder 210 towards the compression chamber 211, with one end penetrating the outer peripheral wall of the cylinder 210 and the other end being a closed end. The second channel 252 is arranged axially along the cylinder 210, extending from the upper end face of the cylinder 210 to the first channel 251. The third channel 253 is disposed on the upper end face (i.e., the axial end face) of the cylinder 210 and is recessed downwards. The third channel 253 is arranged along the thickness direction of the slide 230, or the third channel 253 is inclined at a certain angle relative to the thickness direction of the slide 230. The two ends of the third channel 253 are respectively connected to the upper end of the second channel 252 and the second air supply channel 260. It is easy to understand that the upper opening of the second channel 252 and the upper opening of the third channel 253 are sealed by the first bearing 270 to prevent refrigerant leakage. Therefore, the replenished refrigerant can enter the exhaust chamber 2112 in sequence through the first channel 251, the second channel 252, the third channel 253, and the second air supply channel 260.

[0066] It is understood that in some other embodiments, the second channel 252 extends from the lower end face (also the axial end face) of the cylinder 210 to the first channel 251, and the third channel 253 is disposed on the lower end face of the cylinder 210 and recessed upwards, which will not be described in detail here.

[0067] Understandably, the outline of the cross-section of the first channel 251 can be circular, semi-circular, elliptical, polygonal, etc. Similarly, the outline of the cross-section of the second channel 252 can be circular, semi-circular, elliptical, polygonal, etc. The cross-section of the third channel 253 can be rectangular, trapezoidal, semi-circular, etc., and the shape of the third channel 253 along its length can be straight, curved, broken, etc.

[0068] It is understandable that when machining the first air supply channel 250, the first channel 251 and the second channel 252 are machined by drilling, and the third channel 253 is machined by cutting or milling. The machining method is simple and helps to reduce machining costs.

[0069] Reference Figure 4As shown, it can be understood that the intake port 213 and the first air supply channel 250 are located on both sides of the vane groove 212. The angle between the central axis of the intake port 213 and the central axis of the first channel 251 is defined as θ, satisfying: 20°≤θ≤110°. Generally, the relative position between the intake port 213 and the vane groove 212 is determined. If θ < 20°, the minimum distance between the first channel 251 and the vane groove 212 is too small, affecting the structural strength of the cylinder 210 at the first channel 251 and the vane groove 212, and also resulting in the third channel 253 being too short, leading to poor machinability. If θ > 110°, the total length of the first air supply channel 250 is large, resulting in high airflow resistance, affecting air supply efficiency, and the length of the third channel 253 is too large, increasing the difficulty of machining. Therefore, by ensuring that 20°≤θ≤110°, for example, the value of θ is 30°, 40°, 50°, 80° or 100°, the airflow resistance during the air replenishment process can be reduced, the air replenishment efficiency can be improved, and the machining difficulty of the first air replenishment channel 250 can be reduced, thus improving the machinability, while ensuring the structural strength of the cylinder 210.

[0070] Understandably, the second air supply channel 260 is located between two opposite end faces of the slide vane 230 along the axial direction of the cylinder 210. For example, the second air supply channel 260 is located at the middle position or slightly off-center of the slide vane 230 along the axial direction of the cylinder 210. That is, the second air supply channel 260 only has an opening towards the first air supply channel 250, meaning the second air supply channel 260 is closed on both sides along the axial direction of the cylinder 210, eliminating the need for sealing using the first bearing 270, partition 290, or second bearing 280, which helps reduce the risk of refrigerant leakage. In this case, the second air supply channel 260 can be obtained by milling, which is a simple machining process.

[0071] Reference Figure 6 As shown, it can be understood that in some other embodiments, the second air supply channel 260 extends along the axial direction of the cylinder 210 through one of the two end faces of the slide vane 230. For example, the second air supply channel 260 extends through the upper or lower end face of the slide vane 230. That is, in addition to having an opening towards the first air supply channel 250, the second air supply channel 260 also has an opening at its upper or lower end. In this case, the opening at the upper or lower end of the second air supply channel 260 is sealed by the first bearing 270, the partition 290, or the second bearing 280, resulting in a good sealing effect and a low risk of refrigerant leakage. Similarly, the second air supply channel 260 can be obtained by milling, which is a simple machining process.

[0072] It is understandable that the cross-section of the second air supply channel 260 can be rectangular, trapezoidal, semi-circular, etc., and the shape of the second air supply channel 260 along its length can be straight, curved, or broken.

[0073] It is easy to understand that when the first air supply channel 250 and the second air supply channel 260 are connected to the compression chamber 211, and the first air supply channel 250 and the second air supply channel 260 are not supplying air, the first air supply channel 250 and the second air supply channel 260 are equivalent to an additional clearance volume, which will cause the volumetric efficiency of the compressor 1000 to decrease.

[0074] Reference Figure 3 As shown, it can be understood that the cross-sectional area of ​​the second air supply channel 260 is defined as S4, satisfying: 1mm 2 ≤S4≤25mm 2 The cross-sectional area of ​​the second air supply channel 260 is the area of ​​the cross-section of the second air supply channel 260 perpendicular to its length. By rationally designing the cross-sectional area of ​​the second air supply channel 260, sufficient air supply can be ensured for compressors 1000 of different displacements to enhance the heating effect in low-temperature environments. At the same time, it avoids the disadvantage of a reduced air supply due to an excessively small cross-sectional area of ​​the second air supply channel 260, which would lead to a deterioration in heating performance at low temperatures; and avoids the disadvantage of an excessively large cross-sectional area of ​​the second air supply channel 260, which would lead to a decrease in the structural strength of the sliding vane 230 and a large clearance volume in the compressor 1000, thus affecting the reliability and volumetric efficiency of the compressor 1000. For example, the cross-sectional area S4 of the second air supply channel 260 can be 1 mm². 2 10mm 2 15mm 2 Or 25mm 2 wait.

[0075] It is easy to understand that the cross-sectional area of ​​the second air supply channel 260 is determined based on the displacement of the compressor 1000.

[0076] Reference Figure 3As shown, it can be understood that the cross-sectional area of ​​the third channel 253 is defined as S3, satisfying: 1≤S3 / S4≤2. The cross-sectional area of ​​the third channel 253 is the area of ​​the cross section of the third channel 253 perpendicular to its length. That is, the ratio of the cross-sectional area of ​​the third channel 253 to the cross-sectional area of ​​the second air supply channel 260 is between 1 and 2. Under the premise that the cross-sectional area S4 of the second air supply channel 260 is determined, if S3 / S4<1, the cross-sectional area of ​​the third channel 253 is too small, resulting in a decrease in the air supply volume and affecting the heating effect in low-temperature environments; if S3 / S4>2, the cross-sectional area of ​​the third channel 253 is too large, which on the one hand will lead to a decrease in the structural strength of the cylinder 210 near the vane groove 212, and on the other hand will lead to an increase in the clearance volume and a decrease in the volumetric efficiency of the compressor 1000. Therefore, making 1≤S3 / S4≤2, for example, the value of S3 / S4 is 1, 1.3, 1.7 or 2, can not only enhance the heating effect in low temperature environment, but also reduce the impact of the third channel 253 on the structural strength of cylinder 210 and the volumetric efficiency of compressor 1000.

[0077] Reference Figure 3 As shown, it can be understood that the cross-sectional area of ​​the first channel 251 is defined as S1, satisfying: 1≤S1 / S3≤3. The cross-sectional area of ​​the first channel 251 is the area of ​​the cross section of the first channel 251 perpendicular to its length. That is, the ratio of the cross-sectional area of ​​the first channel 251 to the cross-sectional area of ​​the third channel 253 ranges from 1 to 3. Given that the cross-sectional area S3 of the third channel 253 is determined, if S1 / S3<1, the cross-sectional area of ​​the first channel 251 is too small, resulting in a decrease in the air supply and affecting the heating effect in low-temperature environments; if S1 / S3>3, the cross-sectional area of ​​the first channel 251 is too large, which on the one hand will lead to a decrease in the structural strength of the cylinder 210 near the vane groove 212, and on the other hand will lead to an increase in the clearance volume and a decrease in the volumetric efficiency of the compressor 1000. Therefore, making 1≤S1 / S3≤3, for example, the value of S1 / S3 is 1, 1.7, 2.7 or 3, can not only enhance the heating effect in low temperature environment, but also reduce the impact of the first channel 251 on the structural strength of cylinder 210 and the volumetric efficiency of compressor 1000.

[0078] Reference Figure 3As shown, it can be understood that the minimum cross-sectional area of ​​the second channel 252 is defined as S2, satisfying: 1≤S2 / S3≤3. The cross-sectional area of ​​the second channel 252 is the area of ​​the cross section of the second channel 252 perpendicular to its length. That is, the ratio of the cross-sectional area of ​​the second channel 252 to the cross-sectional area of ​​the third channel 253 ranges from 1 to 3. Given that the cross-sectional area S3 of the third channel 253 is determined, if S2 / S3<1, the cross-sectional area of ​​the second channel 252 is too small, resulting in a decrease in the air supply and affecting the heating effect in low-temperature environments; if S2 / S3>3, the cross-sectional area of ​​the second channel 252 is too large, which on the one hand will lead to a decrease in the structural strength of the cylinder 210 near the vane groove 212, and on the other hand will lead to an increase in the clearance volume and a decrease in the volumetric efficiency of the compressor 1000. Therefore, making 1≤S2 / S3≤3, for example, the value of S2 / S3 is 1, 1.7, 2.7 or 3, can not only enhance the heating effect in low temperature environment, but also reduce the impact of the second channel 252 on the structural strength of cylinder 210 and the volumetric efficiency of compressor 1000.

[0079] Reference Figure 4 and Figure 6 As shown, it can be understood that, along the sliding direction of the slide plate 230, the distance between the end of the second air supply channel 260 facing the compression chamber 211 and the end of the slide plate 230 facing the roller 220 is L1, which satisfies: 2mm≤L1≤10mm. By ensuring L2 ≥ 2mm, on the one hand, the wall thickness of the second air supply channel 260 near the roller 220 is guaranteed to ensure that the structural strength of the vane 230 meets the requirements and improves the reliability of the vane 230; on the other hand, when the exhaust valve plate of the cylinder 210 is open or the pressure of the refrigerant in the exhaust chamber 2112 is greater than the pressure of the refrigerant in the second air supply channel 260, it is prevented that the refrigerant in the exhaust chamber 2112 will flow back to the second liquid reservoir 1200 through the second air supply channel 260 and the first air supply channel 250 because the second air supply channel 260 is too close to the end of the vane 230 near the roller 220. In other words, it prevents the second air supply channel 260 from connecting with the exhaust chamber 2112 at this time, thereby reducing power consumption and improving the efficiency of the compressor 1000. When L2 ≤ 10mm, during the compression process after the intake process, it prevents the second air supply channel 260 from being disconnected from the exhaust chamber 2112 due to the distance between the second air supply channel 260 and the end of the vane 230 near the roller 220 being too far, thus avoiding delayed or non-exhaust air supply. Therefore, 2mm ≤ L1 ≤ 10mm, for example, L1 can be 2mm, 4mm, 7mm, 9mm, or 10mm, which ensures both the structural strength of the vane 230 and prevents airflow deviation, while also ensuring timely air supply to enhance the heating effect in low-temperature environments. It is easy to understand that L1 is smaller than the eccentricity of the roller 220.

[0080] Reference Figure 6 As shown, it can be understood that along the sliding direction of the vane 230, the length of the second air supply channel 260 is L2, and the length of the vane 230 is L3, satisfying: 2mm≤L2≤L3-L1-2. Making L2≥2mm ensures that within the stroke range of the vane 230 (i.e., during the operation of the compressor 1000), the second air supply channel 260 remains connected to the first air supply channel 250, making the force exerted by the supplemented refrigerant on the vane 230 in the thickness direction relatively stable, which is beneficial for maintaining the movement stability of the vane 230 and thus improving reliability. Making L2≤L3-L1-2 ensures the wall thickness of the end of the second air supply channel 260 away from the roller 220, ensuring that the structural strength of the vane 230 meets the requirements and improving the reliability of the vane 230. Therefore, by ensuring that 2mm ≤ L2 ≤ L3 - L1 - 2, the structural strength requirements of the sliding vane 230 are met while improving its movement stability, thereby enhancing the reliability of the compressor 1000. It is easy to understand that L2 is greater than the eccentricity of the roller 220.

[0081] Reference Figure 7 As shown, it is understandable that the thickness of the vane 230 is generally uniform throughout. Let the thickness of the vane 230 be T, and the depth of the second air supply channel 260 along the thickness direction of the vane 230 be H, satisfying: 1mm ≤ H ≤ T / 2. Making H ≥ 1mm avoids the drawback of insufficient air supply due to a small depth (i.e., small cross-sectional area) of the second air supply channel 260, which would lead to a decrease in air supply volume and consequently a deterioration in heating performance at low temperatures. Making H ≤ T / 2 avoids the drawback of excessive depth (i.e., excessive cross-sectional area) of the second air supply channel 260, which would lead to a decrease in the structural strength of the vane 230 and a large clearance volume in the compressor 1000, thus affecting the reliability and volumetric efficiency of the compressor 1000.

[0082] It is understood that the second channel 252 includes a tapered section 2521 that connects to the third channel 253. One end of the tapered section 2521 that connects to the third channel 253 passes through the axial end face of the cylinder 210 that has the third channel 253. The inner diameter of the tapered section 2521 decreases from the third channel 253 to the first channel 251 along the axial direction of the cylinder 210.

[0083] Reference Figure 9 and Figure 10As shown, it can be understood that in some specific embodiments, the second channel 252 penetrates the upper end face of the cylinder 210, and the third channel 253 is disposed on the upper end face of the cylinder 210. The second channel 252 includes a tapered section 2521 located at the upper end, that is, the tapered section 2521 penetrates the upper end face of the cylinder 210, and the inner diameter of the tapered section 2521 decreases from top to bottom. It is easy to understand that the second channel 252 connects to the third channel 253. A tapered pin 2522 is also installed in the second channel 252. Generally speaking, the outer diameter of the tapered pin 2522 decreases from top to bottom, and the outer contour of the tapered pin 2522 matches the inner contour of the tapered section 2521, and the tapered pin 2522 can move up and down within the tapered section 2521 under stress. When the refrigerant pressure (i.e., jet pressure) in the first channel 251 is greater than the sum of the weight of the conical pin 2522 and the refrigerant pressure in the exhaust chamber 2112, the conical pin 2522 moves upward, connecting the second channel 252 and the third channel 253, thereby replenishing refrigerant into the exhaust chamber 2112 to enhance the heating effect in low-temperature environments. When the refrigerant pressure (i.e., jet pressure) in the first channel 251 is less than or equal to the sum of the weight of the conical pin 2522 and the refrigerant pressure in the exhaust chamber 2112, the conical pin 2522 moves downward, and its outer peripheral wall fits against the inner peripheral wall of the conical section 2521, blocking the second channel 252 and the third channel 253. This prevents the refrigerant in the exhaust chamber 2112 from flowing back to the second liquid receiver 1200 through the second replenishment channel 260 and the first replenishment channel 250, thereby reducing power consumption and improving the efficiency of the compressor 1000.

[0084] The heat pump system of the second aspect of this utility model includes the compressor 1000 of the first aspect of this utility model. The heat pump system can be a heat pump air conditioner, a heat pump water heater, etc.

[0085] Since the heat pump system adopts all the technical solutions of the compressor 1000 in the above embodiments, it has at least all the beneficial effects brought about by the technical solutions in the above embodiments.

[0086] The embodiments of the present utility model have been described in detail above with reference to the accompanying drawings. However, the present utility model is not limited to the above embodiments. Within the scope of knowledge possessed by those skilled in the art, various changes can be made without departing from the spirit of the present utility model.

Claims

1. Compressor, characterized in that, include: case; A pump body assembly is disposed within the housing. The pump body assembly includes a cylinder, a roller, a vane, and a crankshaft. The cylinder has a communicating compression chamber and a vane groove. The roller is rotatably disposed in the compression chamber. The vane is slidably disposed in the vane groove. One end of the vane abuts against the outer peripheral wall of the roller or is connected to the roller. The vane divides the compression chamber into an intake chamber and an exhaust chamber. One end of the crankshaft has an eccentric portion connected to the roller. An electric motor assembly includes a stator and a rotor, the rotor being rotatably disposed in the inner hole of the stator, and the rotor being connected to the other end of the crankshaft; The cylinder is provided with a first air supply channel, and the slide is provided with a second air supply channel on the side facing the exhaust chamber. One end of the first air supply channel penetrates the outer peripheral wall of the cylinder. During the movement of the slide, the other end of the first air supply channel is connected to the second air supply channel, and the second air supply channel is intermittently connected to the exhaust chamber.

2. The compressor of claim 1, wherein: The first air supply channel includes a first channel, a second channel, and a third channel connected in sequence. The first channel is arranged radially along the cylinder and penetrates the outer peripheral wall of the cylinder. The second channel is arranged axially along the cylinder. The third channel is located on the axial end face of the cylinder and is connected to the second air supply channel.

3. The compressor of claim 2, wherein: The cross-sectional area of ​​the first channel is S1, and the cross-sectional area of ​​the third channel is S3, satisfying: 1≤S1 / S3≤3.

4. The compressor of claim 2, wherein: The minimum cross-sectional area of ​​the second channel is S2, and the cross-sectional area of ​​the third channel is S3, satisfying: 1≤S2 / S3≤3.

5. The compressor of claim 2, wherein: The cross-sectional area of ​​the second air supply channel is S4, and the cross-sectional area of ​​the third channel is S3, satisfying: 1≤S3 / S4≤2.

6. The compressor of claim 2, wherein: The cylinder is also provided with an air intake hole that connects to the air intake chamber. The angle between the central axis of the air intake hole and the central axis of the first channel is θ, which satisfies: 20°≤θ≤110°.

7. The compressor of claim 2, wherein: The second channel includes a tapered section that connects to the third channel. One end of the tapered section passes through the axial end face of the cylinder, and the inner diameter of the tapered section decreases from the third channel to the first channel along the axial direction of the cylinder. A tapered pin is installed in the tapered section, and the tapered pin is configured to make or break the connection between the second channel and the third channel.

8. The compressor of claim 1, wherein: The second air supply channel is located between two opposite end faces of the sliding vane along the axial direction of the cylinder; or, The second air supply channel passes through one of the two end faces of the slide.

9. The compressor of claim 1, wherein: Along the sliding direction of the slide plate, the distance between the end of the second air supply channel facing the compression chamber and the end of the slide plate facing the roller is L1, which satisfies: 2mm≤L1≤10mm.

10. The compressor of claim 9, wherein: Along the sliding direction of the slide, the length of the second air supply channel is L2, and the length of the slide is L3, satisfying: 2mm≤L2≤L3-L1-2.

11. The compressor of claim 1, wherein: The thickness of the sliding plate is T, and the depth of the second air supply channel along the thickness direction of the sliding plate is H, satisfying: 1mm≤H≤T / 2.

12. The compressor of claim 1, wherein: The cross section of the second air supplementing channel is S4, satisfying: 1mm 2 ≤S4≤25mm 2 .

13. A heat pump system, characterised in that, Includes the compressor as described in any one of claims 1 to 12.

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