Two-stage enthalpy-increasing compressor and working method

Abstract

The invention provides a two-stage enthalpy-increasing compressor and a working method. The compressor comprises a shell and a pump body arranged in the shell. The pump body comprises a first cylinder and a second cylinder, a middle plate is arranged between the first cylinder and the second cylinder, the first cylinder and the second cylinder are respectively provided with a first cylinder cover and a second cylinder cover, and the first cylinder cover and the middle plate are respectively provided with a mixing cavity; the middle plate is further provided with a spraying channel communicated with the mixing cavity of the middle plate, and the spraying channel is connected with a blowdown pipe; during working, a refrigerant is compressed by the first air cylinder and then is divided into two paths, one path is discharged into the first cylinder cover mixing cavity, and the other path is discharged into the middle plate mixing cavity; the primary exhaust gas in the mixing cavity of the middle plate is mixed with the supplemented gas; and the first-stage exhaust gas in the first cylinder cover mixing cavity then enters the intermediate plate mixing cavity, is mixed with the gas in the intermediate plate mixing cavity again, and is sucked by the second cylinder together. Supplementary gas is sprayed into the middle plate mixing cavity, the gas supplementing path is shortened, the loss of the supplemented gas is reduced, and meanwhile gas pulsation is reduced through vertical exhaust of the first air cylinder.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and particularly relates to a two-stage enthalpy-increasing compressor and a working method thereof. Background Art

[0002] Two-stage enthalpy-increasing compressors are currently generally applied to working conditions with heating capacity requirements at ultra-low ambient temperatures. Two-stage enthalpy increase requires good coordination between the first-stage exhaust and the second-stage suction, so as to reduce the first-stage exhaust resistance, improve the second-stage suction efficiency, reduce the along-channel loss of the flow path, and improve the heating capacity of the system. Considering the installation space of the compressor in the system, in the prior art, the flow paths of the first-stage exhaust and the second-stage suction both adopt the internal flow paths of the compressor, that is, internal flow paths are formed by opening holes on the internal components of the compressor. However, the internal structure of the compressor is compact, which easily limits the size of the flow path. Therefore, in order to reduce the pulsation influence of the first-stage exhaust, the second-stage suction, and the gas flowing into the compressor, a mixing chamber is provided on the pump body of the compressor. At the same time, the supplementary gas is sprayed into the mixing chamber and mixed with the gas after preliminary compression. The mixed gas is then discharged after secondary compression. However, the supplementary gas path in the traditional solution is long, the along-channel resistance is large, and the loss of the supplementary gas is large, which in turn affects the supplementary gas effect. Moreover, there are also certain problems with the current method of exhausting gas to the mixing chamber, which easily causes gas pulsation, makes the gas unstable, and in turn affects the performance of the compressor.

[0003] It should be noted that the information disclosed in the background art part of the present application is only intended to deepen the understanding of the general background art of the present application, and should not be regarded as an admission or any form of suggestion that this information constitutes the prior art known to those skilled in the art. Summary of the Invention

[0004] In view of this, the purpose of the present invention is to provide a two-stage enthalpy-increasing compressor and a working method thereof to solve the problems of long supplementary gas path, large loss of supplementary gas, and easy generation of gas pulsation in the two-stage enthalpy-increasing compressor in the prior art.

[0005] To achieve the above purpose, the present invention provides a two-stage enthalpy-increasing compressor, which includes: a housing, a pump body and a motor arranged in the housing; the pump body includes a first cylinder and a second cylinder, an intermediate plate is arranged between the first cylinder and the second cylinder, a first cylinder head is arranged at one end of the first cylinder away from the intermediate plate, a second cylinder head is arranged at one end of the second cylinder away from the intermediate plate, and mixing chambers are arranged on both the first cylinder head and the intermediate plate; the first cylinder is used for exhausting gas to both the mixing chamber of the intermediate plate and the mixing chamber of the first cylinder head at the same time; a spraying channel communicated with its mixing chamber is also arranged on the intermediate plate; the spraying channel is connected to a supplementary gas pipe; the supplementary gas pipe is used for spraying supplementary gas into the mixing chamber of the intermediate plate.

[0006] Optionally, the central axis of the injection channel intersects the central axis of the intermediate plate;

[0007] Alternatively, the central axis of the injection channel neither intersects nor is parallel to the central axis of the intermediate plate, and the outlet direction of the injection channel follows the air flow direction of the primary exhaust of the mixing chamber within the intermediate plate.

[0008] Optionally, the injection channel is arranged parallel to the cross-sectional direction of the intermediate plate, and the cross-section is perpendicular to the central axis of the intermediate plate.

[0009] Optionally, when the central axis of the injection channel neither intersects nor is parallel to the central axis of the intermediate plate, the included angle between the central axis of the injection channel and the radial direction of the mixing chamber of the intermediate plate is less than or equal to 90°.

[0010] Optionally, the injection channel includes a first channel and a second channel that are connected in sequence from outside to inside. The aperture of the first channel is larger than that of the second channel. The gas supply pipe terminates at the first channel and is connected to the first channel by interference fit.

[0011] Optionally, the intermediate plate is of a circular structure, and the injection channel is provided at a corresponding position on the outer side wall surface of the intermediate plate. Alternatively, the intermediate plate is of a non-circular structure, and a boss is provided at a corresponding position on the outer side wall surface of the intermediate plate. The injection channel is provided on the boss, and the outer diameter of the boss is less than or equal to the inner diameter of the housing.

[0012] Optionally, the mixing chamber of the first cylinder head is also communicated with the mixing chamber of the intermediate plate through an air flow channel on the pump body.

[0013] Optionally, a first muffler is installed at one end of the first cylinder head facing away from the first cylinder. The first muffler and the first cylinder head enclose the mixing chamber of the first cylinder head. The air flow channel on the pump body includes through holes on the first cylinder head, through holes on the cylinder block of the first cylinder, and through holes on the intermediate plate that are axially connected in sequence. The through hole on the intermediate plate is communicated with the mixing chamber of the intermediate plate.

[0014] Optionally, the two-stage enthalpy-increasing compressor further satisfies at least one of the following:

[0015] The intermediate plate includes an axially arranged cover plate and a cavity-containing plate. The cover plate and the cavity-containing plate enclose the mixing chamber of the intermediate plate;

[0016] A second muffler is installed at one end of the second cylinder head facing away from the second cylinder;

[0017] The first cylinder is on the side away from the motor, and the second cylinder is on the side close to the motor.

[0018] Based on the same inventive concept, the present invention also provides a working method for a two-stage enthalpy-increasing compressor, which employs the two-stage enthalpy-increasing compressor described in any one of the above, and the working method includes:

[0019] The refrigerant enters the first cylinder. After being compressed by the first cylinder, the gas path of the refrigerant is divided into two paths. One path of the gas is discharged into the mixing cavity of the first cylinder head, and the other path of the gas is discharged into the mixing cavity of the intermediate plate; one path of the gas discharged into the mixing cavity of the intermediate plate is mixed with one path of the supplementary gas injected into the mixing cavity of the intermediate plate by the supplementary gas pipe to form a mixed gas; and one path of the gas discharged into the mixing cavity of the first cylinder head then enters the mixing cavity of the intermediate plate and is inhaled by the second cylinder together with the mixed gas after being remixed.

[0020] As described above, the two-stage enthalpy-increasing compressor and the working method provided by the present invention have the following beneficial effects: The two-stage enthalpy-increasing compressor provided by the present invention includes: a housing, a pump body and a motor arranged in the housing; the pump body includes a first cylinder and a second cylinder, an intermediate plate is arranged between the first cylinder and the second cylinder, a first cylinder head is arranged at one end of the first cylinder away from the intermediate plate, a second cylinder head is arranged at one end of the second cylinder away from the intermediate plate, and both the first cylinder head and the intermediate plate are provided with mixing cavities; the first cylinder is used for exhausting gas to both the mixing cavity of the intermediate plate and the mixing cavity of the first cylinder head at the same time; the intermediate plate is also provided with a spray channel communicated with its mixing cavity; the spray channel is connected to the supplementary gas pipe. In this way, when the two-stage enthalpy-increasing compressor works, the refrigerant enters the first cylinder. After being compressed by the first cylinder, the gas path of the refrigerant is divided into two paths. One path of the gas is discharged into the mixing cavity of the first cylinder head, and the other path of the gas is discharged into the mixing cavity of the intermediate plate; one path of the gas discharged into the mixing cavity of the intermediate plate is mixed with one path of the supplementary gas injected into the mixing cavity of the intermediate plate by the supplementary gas pipe to form a mixed gas; and one path of the gas discharged into the mixing cavity of the first cylinder head then enters the mixing cavity of the intermediate plate and is inhaled by the second cylinder together with the mixed gas after being remixed.

[0021] In this way, on the one hand, when the first cylinder exhausts gas up and down at the same time, the gas discharged into the mixing cavity of the first cylinder head can become relatively stable before entering the mixing cavity of the intermediate plate. Compared with the first cylinder directly exhausting all the gas into the mixing cavity of the intermediate plate, the first-stage exhaust air flow can be stabilized, the gas pulsation can be reduced, and further the loss caused by the gas pulsation in the mixing cavity of the intermediate plate can be reduced. On the other hand, by opening a spray channel on the intermediate plate, the supplementary gas can be directly sprayed into the mixing cavity of the intermediate plate, thereby shortening the supplementary gas path, reducing the loss of the supplementary gas injection gas, and at the same time not affecting the secondary suction; ultimately, the overall heating capacity of the compressor is effectively improved without reducing the overall performance of the compressor.

[0022] In further improvement, when the central axis of the injection channel neither intersects nor is parallel to the central axis of the intermediate plate, and the outlet direction of the injection channel follows the air flow direction of the primary exhaust in the mixing chamber of the intermediate plate, the resistance of the supplementary gas injection can be minimized, and at the same time, the influence on the main air flow of the primary exhaust gas in the mixing chamber of the intermediate plate can be reduced, thereby reducing the air flow loss, ensuring both the amount of supplementary gas and reducing the disturbance to the primary exhaust. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] Those of ordinary skill in the art will understand that the provided drawings are used to better understand the present invention and do not constitute any limitation to the scope of the present invention. Among them:

[0024] Figure 1 FIG. 1 is a schematic structural diagram of a two-stage enthalpy-increasing compressor provided by a preferred embodiment of the present invention, and the illustrated arrow indicates the refrigerant flow path;

[0025] Figure 2 FIG. 2 is a schematic structural diagram of an intermediate plate provided by a preferred embodiment of the present invention;

[0026] Figure 3 FIG. 3 is a schematic structural diagram of an intermediate plate provided by another preferred embodiment of the present invention;

[0027] Figure 4 FIG. 4 is a schematic top view structural diagram of an intermediate plate provided by a preferred embodiment of the present invention, and the central axis of the illustrated injection channel neither intersects nor is parallel to the central axis of the intermediate plate, and the outlet direction of the injection channel follows the air flow direction of the primary exhaust in the mixing chamber of the intermediate plate;

[0028] Figure 5 FIG. 5 is a schematic diagram of the angular relationship between an injection channel and a mixing chamber of an intermediate plate provided by a preferred embodiment of the present invention, and the angle α between the extending direction of the illustrated injection channel and the radial direction of the mixing chamber of the intermediate plate is close to 90°;

[0029] Figure 6 FIG. 6 is a schematic diagram of the angular relationship between an injection channel and a mixing chamber of an intermediate plate provided by another preferred embodiment of the present invention, and the angle α between the extending direction of the illustrated injection channel and the radial direction of the mixing chamber of the intermediate plate is 90°;

[0030] Figure 7 FIG. 7 is a schematic diagram of the angular relationship between an injection channel and a mixing chamber of an intermediate plate provided by still another preferred embodiment of the present invention, and the central axis of the illustrated injection channel intersects the central axis of the intermediate plate, and the injection channel is arranged parallel to the cross-sectional direction of the intermediate plate.

[0031] The reference numerals are explained as follows:

[0032] 1 - housing, 2 - crankshaft, 3 - first cylinder, 4 - second cylinder, 5 - intermediate plate, 510 - primary exhaust hole, 520 - exhaust valve seat, 530 - boss, 51 - cover plate, 52 - cavity - containing plate, 6 - oil sump, 7 - first cylinder head, 8 - second cylinder head, 9 - mixing chamber, 10 - intake pipe, 11 - first muffler, 12 - second muffler, 13 - injection passage, 131 - first passage, 132 - second passage, 14 - make - up air pipe, α - the included angle between the extension direction of the injection passage and the radial direction of the mixing chamber of the intermediate plate, A1 - the direction of the primary exhaust air flow in the mixing chamber of the intermediate plate, A2 - the direction of the make - up air flow at the outlet of the injection passage. Detailed implementation manners

[0033] To make the objectives, advantages and features of the present invention clearer, the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments. It should be noted that the accompanying drawings are all in very simplified forms and not drawn to scale, and are only used to facilitate and clearly assist in explaining the objectives of the embodiments of the present invention. In addition, the structures shown in the accompanying drawings are often part of the actual structures. In particular, the emphases to be shown in each of the accompanying drawings are different, and sometimes different scales are used.

[0034] As used in the present invention, the singular forms "a", "an", "one" and "the" include plural objects, the term "or" is generally used in the sense of including "and / or", the term "several" is generally used in the sense of including "at least one", the term "at least two" is generally used in the sense of including "two or more", in addition, the terms "first" and "second" are only used for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly indicating the quantity of the indicated technical features. Thus, the features defined with "first" and "second" may explicitly or implicitly include one or at least two of such features. "One end" and "the other end" generally refer to corresponding two parts, which not only include the endpoints. In addition, as used in the present invention, "mounted", "connected", "coupled", "a component is'set' on another component" should be understood in a broad sense, and generally only indicates that there is a connection, coupling, cooperation or transmission relationship between two components, and the two components can be directly or indirectly connected, coupled, cooperated or transmitted through an intermediate component, and cannot be understood as indicating or implying the spatial position relationship between the two components, that is, a component can be inside, outside, above, below or on one side of another component in any orientation, unless the content clearly indicates otherwise. For those of ordinary skill in the art, the specific meanings of the above - mentioned terms in the present invention can be understood according to specific circumstances. In addition, directional terms such as above, below, up, down, upward, downward, left, right, etc. are used relative to the exemplary embodiments as shown in the drawings. The upward or upper direction faces the top of the corresponding drawing, and the downward or lower direction faces the bottom of the corresponding drawing.

[0035] The object of the present invention is to provide a two-stage enthalpy-increasing compressor and a working method thereof, so as to solve the problems of long gas replenishing path, large loss of replenishing gas and easy gas pulsation in the two-stage enthalpy-increasing compressor in the prior art.

[0036] In addition, it should be noted that the two-stage enthalpy-increasing compressor provided by the present invention can be a vertical compressor or a horizontal compressor. Only the vertical compressor is taken as an example for illustration below. However, those skilled in the art can clearly understand the technical content of the horizontal compressor according to the content disclosed by the present invention. The following description is made with reference to the accompanying drawings.

[0037] Figure 1 The structural schematic diagram of the two-stage enthalpy-increasing compressor provided by some embodiments of the present invention is shown. As Figure 1 shown, the two-stage enthalpy-increasing compressor includes a housing 1, a motor and a pump body disposed inside the housing 1. Although the motor is not shown in the drawings, those skilled in the art should be able to understand the structure and arrangement of the motor. Here, it will not be described in detail.

[0038] Specifically, the pump body includes: a crankshaft 2; a first cylinder 3 and a second cylinder 4 sleeved on the crankshaft 2; and an intermediate plate 5 located between the first cylinder 3 and the second cylinder 4. Among them: the crankshaft 2 also extends into the rotor of the motor.

[0039] As can be understood by those skilled in the art, the motor is composed of a stator and a rotor disposed inside the stator. After the stator of the motor is powered on and starts, the rotor rotates, and the rotor drives the crankshaft 2 of the pump body to rotate. The rotation of the crankshaft 2 drives the rolling piston in the pump body cylinder to rotate eccentrically.

[0040] In this embodiment, the first cylinder 3 is on the side away from the motor, while the second cylinder 4 is on the side close to the motor. It should be noted that in other embodiments, the first cylinder 3 can be on the side close to the motor, and the second cylinder 4 can be on the side away from the motor. Preferably, the first cylinder 3 is the lower cylinder, and the second cylinder 4 is the upper cylinder.

[0041] Furthermore, one end of the first cylinder 3 facing away from the intermediate plate 5 is provided with a first cylinder head 7, and both the intermediate plate 5 and the first cylinder head 7 are sealed in cooperation with the first cylinder 3. At the same time, one end of the second cylinder 4 facing away from the intermediate plate 5 is provided with a second cylinder head 8, and both the intermediate plate 5 and the second cylinder head 8 are sealed in cooperation with the second cylinder 4. Preferably, the first cylinder head 7 is the lower cylinder head, and the second cylinder head 8 is the upper cylinder head.

[0042] The two-stage enthalpy-increasing compressor provided by this embodiment is preferably a vertical compressor, and an oil sump 6 is provided at the bottom of the housing 1.

[0043] It should also be understood that, compared with other twin-cylinder compressors, the force exerted on the crankshaft 2 by the two cylinders of the two-stage enthalpy-increasing compressor is usually lower. Therefore, the displacement of the two-stage enthalpy-increasing compressor can be maximally and reasonably set. The displacement of the two-stage enthalpy-increasing compressor is actually the displacement of the first cylinder 3, and the first-stage displacement is designed as large as possible to the limit displacement of the compressor with the same shell diameter, that is, the limit cylinder height is adopted under the same cylinder diameter. Considering that both the clearance volume and heat loss will increase after the cylinder height increases, for this reason, the first cylinder 3 adopts the upper and lower exhaust mode. Compared with the single-side exhaust, it can effectively improve the volumetric efficiency of the compressor, increase the overall heating capacity, and at the same time ensure the overall performance of the compressor.

[0044] Specifically, in combination with Figure 1 , the refrigerant path during the operation of the two-stage enthalpy-increasing compressor in this embodiment is as shown by the arrows in the figure. The first cylinder 3 is the first-stage cylinder, the second cylinder 4 is the second-stage cylinder, and the first cylinder 3 exhausts both upward and downward at the same time. Specifically: both the intermediate plate 5 and the first cylinder head 7 are provided with a mixing cavity 9. When the compressor operates, the first cylinder 3 exhausts gas to the mixing cavity 9 of the intermediate plate 5 and the mixing cavity 9 of the first cylinder head 7 at the same time.

[0045] It should also be noted that although it is described as the mixing cavity 9 of the first cylinder head 7, this mixing cavity 9 can be arranged inside the first cylinder head 7, or outside the first cylinder head 7, or both inside and outside the first cylinder head 7 at the same time.

[0046] In addition, when the first cylinder 3 adopts the upper and lower exhaust mode, since the mixing cavity 9 of the intermediate plate 5 is the position in the pump body that is closest to the first-stage exhaust and the second-stage suction and where the mixing cavity 9 can be designed at the same time, therefore, the mixing cavity 9 of the intermediate plate 5 is also necessary to reduce the along-flow resistance of the gas flow from the first stage to the second stage. Specifically, when the first cylinder 3 exhausts both upward and downward at the same time, the gas discharged into the mixing cavity 9 of the first cylinder head 7 can become relatively stable in this mixing cavity 9 and then enter the mixing cavity 9 of the intermediate plate 5. Compared with the first cylinder 3 directly discharging all the gas into the mixing cavity 9 of the intermediate plate 5, it can stabilize the first-stage exhaust, reduce gas pulsation, and further reduce the loss caused by gas pulsation in the mixing cavity 9 of the intermediate plate 5. Therefore, setting the first cylinder 3 to exhaust gas to the mixing cavity 9 adjacent to the first cylinder head 7 and the mixing cavity 9 adjacent to the intermediate plate 5 at the same time is very beneficial for stabilizing the first-stage exhaust gas flow and reducing gas pulsation.

[0047] Moreover, an injection channel 13 communicating with the mixing chamber 9 is provided on the intermediate plate 5, and the injection channel 13 is connected to the gas supply pipe 14. Thus, when the compressor operates, the gas supply gas is directly injected into the mixing chamber 9 of the intermediate plate 5 through the gas supply pipe 14 and the injection channel 13, thereby realizing gas injection and enthalpy increase. In this way, the gas supply gas can be directly injected into the mixing chamber 9 of the intermediate plate 5. Compared with the case where all the gas is injected into the mixing chamber 9 of the first cylinder head 7, the gas supply path is shortened, the loss of the gas injection for gas supply is reduced, the effect of gas injection and enthalpy increase is ensured, and the heating capacity of the compressor is effectively improved.

[0048] As Figure 1 shown, in this embodiment, the gas supply pipe 14 passes through the housing 1 and extends to the inside of the housing 1, and is connected to the injection channel 13 on the intermediate plate 5. The gas supply pipe 14 is usually made of copper pipe. In addition, the connection manner between the injection channel 13 and the gas supply pipe 14 is preferably interference fit connection, which can not only ensure the sealing performance, but also be convenient for installation and use. Moreover, the connection structure is simple, the connection precision is high, and the connection stability is good. When using interference fit connection, the gas supply pipe 14 is made of a material with lower rigidity, preferably copper pipe, and then a reasonable interference size is set to make the gas supply pipe 14 deformed to have an interference fit with the injection channel 13.

[0049] The injection channel 13 is a through-hole structure, and the cross-section of the injection channel 13 is preferably circular, which is convenient for processing and installing the gas supply pipe 14. In addition, the injection channel 13 adopts at least one of a straight through-hole and a curved through-hole. More preferably, the injection channel 13 is a straight through-hole.

[0050] As Figure 4 and Figure 7 shown, considering the assembly problem, in this embodiment, the injection channel 13 includes a first hole 131 and a second hole 132 that are connected in sequence from outside to inside. The aperture of the first hole 131 is larger than that of the second hole 132, and the gas supply pipe 14 terminates at the first hole 131 and is connected to the first hole 131 by interference fit.

[0051] It should also be understood that a mixing chamber 9 with a circular cross-section is provided inside the intermediate plate 5, and an injection channel 13 is provided on the chamber wall of the mixing chamber 9 of the intermediate plate 5. The central axis of the injection channel 13 intersects with the central axis of the intermediate plate 5 (see Figure 7 ), or the central axis of the injection channel 13 neither intersects nor is parallel to the central axis of the intermediate plate 5 (i.e., skew, see details in Figures 4 to 6 ).

[0052] When the central axis of the injection channel 13 intersects the central axis of the intermediate plate 5, the injection channel 13 can be set in a horizontal direction, an obliquely upward direction, or an obliquely downward direction, preferably the horizontal direction. Similarly, when the central axis of the injection channel 13 neither intersects nor is parallel to the central axis of the intermediate plate 5, the injection channel 13 can be set in a horizontal direction, an obliquely upward direction, or an obliquely downward direction, preferably the horizontal direction.

[0053] Specifically, please refer to Figures 4 to 7 , when viewed from the cross-sectional direction parallel to the intermediate plate 5, the extending direction of the injection channel 13 is set at an angle α with the radial direction of the mixing chamber 9 of the intermediate plate 5. Here, the extending direction refers to the direction from the inlet to the outlet of the injection channel 13, where: the angle α is set to 0° to 90°. When the angle α is 0°, that is, the central axis of the injection channel 13 intersects the central axis of the intermediate plate 5; when the angle α is not 0°, that is, the central axis of the injection channel 13 neither intersects nor is parallel to the central axis of the intermediate plate 5, and at this time, the angle α ≤ 90°.

[0054] Here, the radial direction of the mixing chamber 9 of the intermediate plate 5 refers to the direction of the connection line between the connection point a of the injection channel 13 and the mixing chamber 9 and the center O of the mixing chamber 9. Specifically, the angle α is the angle between the central axis of the injection channel 13 and the radius of the mixing chamber 9 at the connection point a of the injection channel 13. Similarly, if the central axis of the injection channel 13 is a curve, it is considered the angle between the tangent line at the connection point a of the central axis and the radius. Particularly, the central axis of the injection channel 13 can also not intersect the cavity wall of the mixing chamber 9 of the intermediate plate 5, that is, the central axis of the injection channel 13 deviates outside the mixing chamber 9. At this time, the angle α is also defined as 90°. This content can be seen in Figure 6 .

[0055] In particular, when the central axis of the injection channel 13 neither intersects nor is parallel to the central axis of the intermediate plate 5, and the outlet direction of the injection channel 13 follows the air flow direction of the primary exhaust of the mixing chamber 9 in the intermediate plate 5 (see the arrow A1 in Figure 4 ), the resistance of the supplementary air injection can be minimized as much as possible, and at the same time, the influence on the main air flow of the primary exhaust gas in the mixing chamber 9 of the intermediate plate 5 can be reduced, thereby reducing the air flow loss, ensuring both the amount of supplementary air and reducing the disturbance to the primary exhaust. Thus, since the cavity wall of the mixing chamber 9 in the intermediate plate 5 is an arc surface, the supplementary air is preferably injected along the tangent direction of the arc of the cavity wall, which can better reduce the resistance of the supplementary air (the arrow A2 represents the injection direction of the supplementary air) injected into the mixing chamber 9, and at the same time better reduce the influence on the primary exhaust gas in the mixing chamber 9.

[0056] Further, for easier assembly and processing, the injection channel 13 is preferably arranged parallel to the cross-sectional direction of the intermediate plate 5, where the cross-section of the intermediate plate 5 is perpendicular to the central axis of the intermediate plate 5. For example, Figure 7 As shown, when the central axis of the injection channel 13 intersects the central axis of the intermediate plate 5, the injection channel 13 is directly machined in the radial direction of the intermediate plate 5. Then, when installing the gas supply pipe 14, the gas supply pipe 14 can be directly pressed into the injection channel 14 in the radial direction.

[0057] Another example is Figures 4 to 6 As shown, when the central axis of the injection channel 13 neither intersects nor is parallel to the central axis of the intermediate plate 5, the injection channel 13 is directly machined in the cross-sectional direction of the intermediate plate 5, avoiding drilling obliquely upward or downward to form the injection channel 13. At this time, when installing the gas supply pipe 14, a corresponding fixture can be used to prevent circumferential rotation, and then the gas supply pipe 14 can be pressed into the injection channel 14.

[0058] On the other hand, based on the same inventive concept, this embodiment also provides a working method for a two-stage enthalpy-increasing compressor, specifically: the refrigerant enters the first cylinder 3, and after being compressed by the first cylinder 3, the gas path of the refrigerant is divided into two paths. One path of gas is discharged into the mixing chamber 9 of the first cylinder head 7, and the other path of gas is discharged into the mixing chamber 9 of the intermediate plate 5; one path of gas discharged into the mixing chamber 9 of the intermediate plate 5 is mixed with one path of supplementary gas injected into the mixing chamber 9 of the intermediate plate 5 by the gas supply pipe 14 to form a mixed gas; and one path of gas discharged into the mixing chamber 9 of the first cylinder head 7 then enters the mixing chamber 9 of the intermediate plate 5 and is mixed with the mixed gas in the mixing chamber 9 of the intermediate plate 5 again, and then is jointly sucked by the second cylinder 4.

[0059] Specifically, in this embodiment, the gas path during operation is as follows: the refrigerant enters the first cylinder 3 from the suction pipe 10 on the housing 1. After being compressed by the first cylinder 3, one path is discharged into the mixing chamber 9 of the first cylinder head 7, and the other path is discharged into the mixing chamber 9 of the intermediate plate 5. One path of gas discharged into the mixing chamber 9 of the intermediate plate 5 is mixed with one path of supplementary gas directly injected into the mixing chamber 9 of the intermediate plate 5 to form a mixed gas. And one path of gas discharged into the mixing chamber 9 of the first cylinder head 7 is initially stabilized in the mixing chamber 9 of the first cylinder head 7, and then enters the mixing chamber 9 of the intermediate plate 5 through the gas flow channel on the pump body and is mixed with the mixed gas in the mixing chamber 9 of the intermediate plate 5 again. At this point, the two paths of gas from the first-stage exhaust are merged and jointly sucked by the second cylinder 4 together with an additional path of supplementary gas.

[0060] It should be understood that if the air supplement injection air flow is directly designed at the secondary air intake of the second cylinder 4, losses may occur to the secondary air intake; if the air supplement injection air flow is directly designed in the mixing chamber 9 of the first cylinder head 7, since the gas in the mixing chamber 9 of the first cylinder head 7 still needs to converge into the mixing chamber 9 of the intermediate plate 5 before being inhaled by the second cylinder 4, the air supplement path is long at this time, and it is easier to cause losses to the air supplement injection air flow. Therefore, in the present invention, the air supplement injection air flow is directly designed in the mixing chamber 9 of the intermediate plate 5 closest to the secondary air intake, realizing air supplement to the mixing chamber 9 of the intermediate plate 5, avoiding the influence on the secondary air intake and reducing the loss of the air supplement injection gas.

[0061] In addition, since the mixing chamber 9 is provided on both the intermediate plate 5 and the first cylinder head 7, the total volume of the mixing chamber 9 is increased, which is beneficial to stabilizing the exhaust air flow of the first cylinder 3 and further improving the performance of the compressor. Specifically, the increase in the mixing chamber 9 mainly stabilizes the exhaust air flow of the first cylinder 3. However, if the mixing chamber 9 of the intermediate plate 5 is set too large, it is necessary to increase the height of the intermediate plate 5, resulting in an increase in the distance between the two eccentric parts of the crankshaft 2 and increasing the risk of force deformation of the crankshaft 2. Therefore, the mixing chamber 9 of the first cylinder head 7 is added. In this way, it is not necessary to increase the height of the intermediate plate 5, and the total volume of the mixing chamber 9 can be increased. The total volume of the mixing chamber 9 is not the larger the better. In fact, under different working conditions and different rotational speeds, there is an optimal volume design for the mixing chamber 9. However, two-stage enthalpy-increasing compressors generally need to cope with a wider ambient temperature range than ordinary compressors and need to be applied under ultra-low and ultra-high ambient temperatures. Therefore, the application ranges of pressure difference, pressure ratio, and rotational speed are very wide, and it is impossible to use the same total volume of the mixing chamber 6 to cope with each working condition. Therefore, the present invention does not limit the size of the total volume of the mixing chamber 9, and the specific total volume can be reasonably selected according to the actual working conditions.

[0062] As Figure 4 shown, in this embodiment, one end of the intermediate plate 5 facing the first cylinder 3 is axially provided with a primary exhaust hole 510. The mixing chamber 9 of the intermediate plate 5 is communicated with the first cylinder 3 through the primary exhaust hole 510, and an exhaust valve seat 520 is provided at the primary exhaust hole 510. An exhaust valve plate can be arranged on the exhaust valve seat 520. One end of the exhaust valve plate is fixed on the exhaust valve seat 520, and the other end is arranged at the primary exhaust hole 510. During exhaust, the exhaust valve plate is opened, and the first cylinder 3 exhausts gas to the mixing chamber 9 of the intermediate plate 5 through the primary exhaust hole 510, and the exhaust direction is basically limited by the direction of the exhaust valve plate.

[0063] For introducing the gas into the mixing chamber 9 of the first cylinder head 7, one end of the intermediate plate 5 facing the first cylinder is also axially provided with a mixing exhaust hole, and the mixing chamber 9 of the intermediate plate 5 is communicated with the mixing chamber 9 at the first cylinder head 7 through the mixing exhaust hole. The mixing exhaust hole and the primary exhaust hole 510 are separately arranged.

[0064] To achieve up and down exhaust, the first cylinder head 7 is also provided with a primary exhaust hole axially, and the mixing chamber 9 of the first cylinder head 7 communicates with the first cylinder 3 through its primary exhaust hole.

[0065] Furthermore, in this embodiment, the mixing chamber 9 of the first cylinder head 7 is also communicated with the mixing chamber 9 of the intermediate plate 5 through the air flow channel on the pump body, so that one path of the gas discharged into the mixing chamber 9 of the first cylinder head 7 then enters the mixing chamber 9 of the intermediate plate 5 through the air flow channel on the pump body. Here, the air flow channel on the pump body at least includes: a through hole opened on the first cylinder head 7, a through hole opened on the cylinder block of the first cylinder 3, and a through hole opened on the intermediate plate 5, and these through holes are axially communicated in sequence.

[0066] Preferably, as Figure 1 shown, a first muffler 11 is installed at one end of the first cylinder head 7 facing away from the first cylinder 3, and the first muffler 11 and the first cylinder head 7 enclose the mixing chamber 9 of the first cylinder head 7. In this embodiment, the mixing chamber 9 is directly arranged on the outer side of the first cylinder head 7 and the inner side of the first muffler 11. This structure is easy to assemble and process, which is beneficial to reducing the processing cost and assembly difficulty.

[0067] Of course, it is not limited in practice. In other alternative embodiments, the structure of the first cylinder head 7 itself directly encloses the mixing chamber 9. For example, the first cylinder head 7 is set as two parts processed separately. An annular groove is arranged on one part, and the other part is set as a structure similar to a cover plate. After these two parts are joined, they are sealed to form the mixing chamber 9. At this time, the first muffler 11 can be considered to be omitted. Or, an annular groove still remains on the first cylinder head 7, but the first muffler 11 acts as the function of the cover plate to seal the first cylinder head 7 to form the mixing chamber 9.

[0068] In short, the setting method of the mixing chamber 9 of the first cylinder head 7 described in the above embodiments is only used to provide a further understanding of the present invention, and does not constitute an improper limitation to the present invention.

[0069] Optionally, a second muffler 12 is installed at one end of the second cylinder head 8 facing away from the second cylinder 4. The air flow channel on the second cylinder head 8 is communicated with the cavity of the second muffler 12, so that the gas compressed by the second cylinder 4 is directly discharged into the cavity of the second muffler 12 through the air flow channel on the second cylinder head 8, and the compressed gas in the second muffler 12 is directly discharged into the housing 1. Preferably, the first muffler 11 is a lower muffler, and the second muffler 12 is an upper muffler.

[0070] It should also be understood that a first air inlet and a first air outlet are provided on the cylinder block of the first cylinder 3; a second air inlet and a second air outlet are provided on the cylinder block of the second cylinder 4; the first air inlet is communicated with the air suction pipe 10; the first air outlet is communicated with the mixing chamber 9 of the intermediate plate 5 and the first cylinder head 7; the second air inlet is communicated with the exhaust hole on the intermediate plate 5; the second air outlet is generally communicated with the air flow channel on the second cylinder head 8.

[0071] The intermediate plate 5 will be further described below.

[0072] In some embodiments, the intermediate plate 5 is of an overall circular structure, and the injection channel 13 is directly arranged at the corresponding position on the outer side wall surface of the intermediate plate 5. At this time, on the premise of keeping the outer diameter of the existing intermediate plate 5 unchanged, by appropriately reducing the diameter of the mixing chamber 9 and increasing the wall thickness of the outer side wall surface of the mixing chamber 9, the wall thickness can meet the sealing distance requirements between the injection channel 13 and the air supply pipe 14.

[0073] In another alternative embodiment, the intermediate plate 5 adopts a non-circular structure (see key points in Figure 1 and Figure 4 ), and a boss 530 is arranged at the corresponding position on the outer side wall surface of the intermediate plate 5, and the injection channel 13 is arranged on the boss 530. In this implementation scheme, the base body of the intermediate plate 5 is still circular in shape, but a boss 530 is machined on a part of the outer side wall surface of the circular base body, so as to thicken a part of the outer side wall surface of the intermediate plate 5, and make the wall thickness at the boss 530 meet the sealing distance requirements between the air supply pipe 14 and the injection channel 13. The outer diameter of the boss 530 is less than or equal to the inner diameter of the housing 1.

[0074] Actually, from the perspective of processing, the first method has relatively low cost and is the optimal choice for the intermediate plate 5.

[0075] When specifically setting, the intermediate plate 5 may include two-layer, three-layer components or other geometric structures as shown in the figure. The following is a demonstration.

[0076] Such as Figure 2As shown, in a demonstration example provided by the present invention, the intermediate plate 5 is a two-layer component, including an axially arranged cover plate 51 and a cavity plate 52; the cover plate 51 is arranged between the cavity plate 52 and the second cylinder 4, and is respectively sealed in cooperation with the cavity plate 52 and the second cylinder 4; the cavity plate 52 is sealed in cooperation with the first cylinder 3; both the cover plate 51 and the cavity plate 52 are circular ring structures, and their outer diameters are the same; an annular groove (not marked) is machined on the end surface of the cavity plate 52; the cover plate 51 and the cavity plate 52 enclose to form a mixing cavity 9. At this time, an exhaust hole is arranged on the cover plate 51, and the exhaust hole on the cover plate 51 is arranged at the position of the second-stage air intake of the second cylinder 4, so that the mixed gas in the mixing cavity 9 of the intermediate plate 5 is discharged into the second cylinder 4 through the exhaust hole on the cover plate 51. Alternatively, the cavity plate 52 adopts a non-circular structure, and a boss 530 is directly formed by thickening a part of the side wall surface of the cavity plate 52, and the boss 530 protrudes more radially than the remaining side walls of the cavity plate 52.

[0077] Moreover, Figure 2 The structure of the shown intermediate plate 5 can also be set conversely, that is, the cover plate 51 is arranged between the cavity plate 52 and the first cylinder 3, and is respectively sealed in cooperation with the cavity plate 52 and the first cylinder 3; the cavity plate 52 is sealed in cooperation with the second cylinder 4. In this implementation, the annular groove on the cavity plate 52 faces the direction of the first cylinder 3, and the exhaust hole is arranged on the cavity plate 52, so that the mixed gas in the mixing cavity 9 of the intermediate plate 5 is discharged into the second cylinder 4 through the exhaust hole on the cavity plate 52.

[0078] Two cover plates 51 can also be arranged on the intermediate plate 5, as shown in Figure 3 . A cover plate 51 is arranged on both sides of the cavity plate 52, and an annular through groove is directly opened in the middle cavity plate 52, and the two sides of the annular through groove are sealed by two cover plates 51 to form a mixing cavity 9.

[0079] It should be noted that, the intermediate plate 5 described in the above embodiments is only used to provide a further understanding of the present invention, and does not constitute an improper limitation of the present invention. In fact, the structure of the intermediate plate 5 disclosed in the present invention includes but is not limited to the cases exemplified above. However, from the perspective of assembly and cost, the intermediate plate 5 preferably consists of a cover plate 51 and a cavity plate 52.

[0080] In summary, the present invention provides a two-stage enthalpy-increasing compressor, which includes a housing 1, a pump body and a motor disposed in the housing 1; the pump body includes a first cylinder 3 and a second cylinder 4; an intermediate plate 5 is disposed between the first cylinder 3 and the second cylinder 4, and a first cylinder head 7 is provided at one end of the first cylinder 3 facing away from the intermediate plate 5, and a second cylinder head 8 is provided at one end of the second cylinder 4 facing away from the intermediate plate 5. Both the first cylinder head 7 and the intermediate plate 5 are provided with a mixing chamber 9; the first cylinder 3 is used to exhaust gas to the mixing chamber 9 of the intermediate plate 5 and the mixing chamber 9 of the first cylinder head 7 simultaneously; an injection channel 13 communicating with its mixing chamber 9 is further provided on the intermediate plate 5; the injection channel 13 is connected to a supplementary gas pipe 14.

[0081] Based on this, when the two-stage enthalpy-increasing compressor provided by the present invention is working, the refrigerant enters the first cylinder 3. After being compressed by the first cylinder 3, the gas path of the refrigerant is divided into two paths. One path of gas is discharged into the mixing chamber 9 of the first cylinder head 7, and the other path of gas is discharged into the mixing chamber 9 of the intermediate plate 5; one path of gas discharged into the mixing chamber 9 of the intermediate plate 5 is mixed with one path of supplementary gas injected into the mixing chamber 9 of the intermediate plate 5 by the supplementary gas pipe 14 to form a mixed gas; and one path of gas discharged into the mixing chamber of the first cylinder head 7 then enters the mixing chamber 9 of the intermediate plate 5 and is mixed with the mixed gas again and then is jointly inhaled by the second cylinder 4.

[0082] It can be seen that for the two-stage enthalpy-increasing compressor provided by the present invention, on the one hand, when the first cylinder 3 exhausts gas up and down simultaneously, the primary exhaust gas flow can be stabilized, the gas pulsation can be reduced, and further the loss caused by gas pulsation in the mixing chamber 9 of the intermediate plate 5 can be reduced. On the other hand, since the supplementary gas is directly injected into the mixing chamber 9 of the intermediate plate 5, the supplementary gas path is shortened, the loss of the supplementary injection gas is reduced, and at the same time, it has no influence on the secondary suction; ultimately, both the overall heating capacity of the compressor is effectively improved and the overall performance of the compressor is not reduced.

[0083] Particularly, when the central axis of the injection channel 13 neither intersects nor is parallel to the central axis of the intermediate plate 5, and the outlet direction of the injection channel 13 follows the gas flow direction of the primary exhaust in the mixing chamber 9 of the intermediate plate 5, the resistance of the supplementary gas injection can be minimized as much as possible, and at the same time, the influence on the primary exhaust gas in the mixing chamber 9 of the intermediate plate 5 can be reduced, so as to reduce the gas flow loss, ensure the amount of supplementary gas, reduce the disturbance to the primary exhaust, and further improve the performance and heating capacity of the compressor.

[0084] The above description is only a description of the preferred embodiments of the present invention and does not limit the scope of the present invention in any way. Any changes and modifications made by those of ordinary skill in the technical field of the present invention based on the above disclosure shall fall within the protection scope of the technical solution of the present invention.

Claims

1. A two-stage enthalpy-increasing compressor, comprising: A housing, a pump body and an electric motor disposed within the housing. The pump body includes a first cylinder and a second cylinder. An intermediate plate is disposed between the first cylinder and the second cylinder. A first cylinder head is provided at one end of the first cylinder facing away from the intermediate plate, and a second cylinder head is provided at one end of the second cylinder facing away from the intermediate plate. It is characterized in that the first cylinder head and the intermediate plate are both provided with mixing chambers; the first cylinder is used to exhaust gas to the mixing chamber of the intermediate plate and the mixing chamber of the first cylinder head simultaneously; a jet channel communicating with its mixing chamber is further provided on the intermediate plate; the jet channel is connected to a supplementary air pipe.

2. The two-stage enhanced enthalpy compressor according to claim 1, characterized in that, The central axis of the jet channel intersects the central axis of the intermediate plate; Alternatively, the central axis of the jet channel neither intersects nor is parallel to the central axis of the intermediate plate, and the outlet direction of the jet channel follows the air flow direction of the primary exhaust in the mixing chamber of the intermediate plate.

3. The two-stage enthalpy-increasing compressor according to claim 2, characterized in that, The jet channel is arranged parallel to the cross-sectional direction of the intermediate plate, and the cross-section is perpendicular to the central axis of the intermediate plate.

4. The two-stage enthalpy-increasing compressor according to claim 3, characterized in that, When the central axis of the jet channel neither intersects nor is parallel to the central axis of the intermediate plate, the angle between the central axis of the jet channel and the radial direction of the mixing chamber of the intermediate plate is less than or equal to 90°.

5. The two-stage enthalpy-increasing compressor according to any one of claims 1-4, characterized in that The jet channel includes a first pore and a second pore that are sequentially communicated from the outside to the inside. The aperture of the first pore is larger than that of the second pore. The supplementary air pipe terminates at the first pore and is connected to the first pore by interference fit.

6. The two-stage enthalpy-increasing compressor according to any one of claims 1-4, characterized in that, The intermediate plate is of a circular structure, and the jet channel is provided at a corresponding position on the outer wall surface of the intermediate plate. Alternatively, the intermediate plate is of a non-circular structure, and a boss is provided at a corresponding position on the outer wall surface of the intermediate plate. The jet channel is provided on the boss, and the outer diameter of the boss is less than or equal to the inner diameter of the housing.

7. The two-stage enthalpy-increasing compressor according to claim 1 or 2, characterized in that, The mixing chamber of the first cylinder head is further communicated with the mixing chamber of the intermediate plate through an air flow channel on the pump body.

8. The two-stage enthalpy-increasing compressor according to claim 7, wherein A first silencer is installed at one end of the first cylinder head facing away from the first cylinder. The first silencer and the first cylinder head enclose the mixing chamber of the first cylinder head. The air flow channel on the pump body includes through holes on the first cylinder head, through holes on the cylinder body of the first cylinder, and through holes on the intermediate plate that are sequentially communicated axially. The through hole on the intermediate plate is communicated with the mixing chamber of the intermediate plate.

9. The two-stage enthalpy-increasing compressor according to claim 1 or 2, wherein The two-stage enthalpy-increasing compressor further satisfies at least one of the following: The intermediate plate includes an axially arranged cover plate and a cavity plate. The cover plate and the cavity plate enclose to form the mixing chamber of the intermediate plate; A second silencer is installed at one end of the second cylinder head facing away from the second cylinder; The first cylinder is on the side away from the motor, and the second cylinder is on the side close to the motor.

10. A working method of a two-stage enthalpy-increasing compressor, characterized in that, Adopt the two-stage enthalpy-increasing compressor according to any one of claims 1-9, and the working method includes: The refrigerant enters the first cylinder. After being compressed by the first cylinder, the gas path of the refrigerant is divided into two paths. One path of the gas is discharged into the mixing chamber of the first cylinder head, and the other path of the gas is discharged into the mixing chamber of the intermediate plate. One path of the gas discharged into the mixing chamber of the intermediate plate is mixed with one path of the supplementary gas injected into the mixing chamber of the intermediate plate by the supplementary gas pipe to form a mixed gas. And one path of the gas discharged into the mixing chamber of the first cylinder head then enters the mixing chamber of the intermediate plate and is mixed with the mixed gas again and then is jointly inhaled by the second cylinder.

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