Compressor

Abstract

The invention provides a compressor. The compressor comprises a shell and a pump body arranged in the shell. The pump body comprises a first-stage air cylinder, a second-stage air cylinder, a mixing cavity and an injection pipe. A middle plate is arranged between the first-stage cylinder and the second-stage cylinder; the mixing cavity is connected with an injection pipe which is used for injecting supplemented gas to the mixing cavity; refrigerants compressed by the first-stage air cylinder are discharged into the mixing cavity and then sucked into the second-stage air cylinder through the mixing cavity; wherein the displacement of the compressor is V1, the total volume of the mixing cavity is V2, and V2 / V1 is larger than 7 and smaller than or equal to 12. According to the invention, the gas pulsation can be reduced, the compressor is allowed to suck more supplemented gas, the input force of the compressor can also be considered, and the performance of the compressor can also be ensured while the heating capacity of the system is effectively improved.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and particularly to a compressor with an enthalpy-increasing function. Background Art

[0002] Enthalpy-increasing compressors are widely used in the field of ultra-low temperature heating, which can greatly reduce the energy consumption of the system in ultra-low temperature environments, improve the energy efficiency ratio of the system, and have a wide working temperature range, making it adaptable to various low-temperature environments. Among them, two-stage enthalpy-increasing compressors are the main representatives. Existing two-stage enthalpy-increasing compressors mostly adopt a structure with an internal mixing chamber. After the supplementary gas is injected into the mixing chamber, it mixes with the first-stage exhaust gas to form a mixed gas, and then the mixed gas is jointly inhaled by the second-stage cylinder. However, when the existing two-stage enthalpy-increasing compressor works, it is easy to cause the loss of the first-stage exhaust gas flow and increase the gas flow pulsation, which will ultimately affect the heating of the system and is difficult to meet the heating requirements in ultra-low environments.

[0003] It should be noted that the information disclosed in the background art part of this application is only intended to deepen the understanding of the general background art of this 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] The purpose of the present invention is to provide a compressor to solve the problems of large gas loss and large gas flow pulsation existing in the existing two-stage enthalpy-increasing compressor, which in turn cause large heat loss.

[0005] To solve the above technical problems, the present invention provides a compressor, which includes: a housing and a pump body disposed inside the housing; the pump body includes a first-stage cylinder, a second-stage cylinder, a mixing chamber, and a spray pipe; an intermediate plate is provided between the first-stage cylinder and the second-stage cylinder; the mixing chamber is connected to the spray pipe, and the spray pipe is used to spray supplementary gas into the mixing chamber; and the refrigerant compressed by the first-stage cylinder is discharged into the mixing chamber and then inhaled by the second-stage cylinder from the mixing chamber, where: the displacement of the compressor is V1, the total volume of the mixing chamber is V2, and 7 < V2 / V1 ≤ 12.

[0006] Optionally, 7.1 ≤ V2 / V1 ≤ 12.

[0007] Optionally, a first cylinder head is provided at one end of the first-stage cylinder away from the intermediate plate, a second cylinder head is provided at one end of the second-stage cylinder away from the intermediate plate, and the mixing chamber is provided on both the intermediate plate and the first cylinder head; the first-stage cylinder is configured to exhaust gas into both the mixing chamber on the intermediate plate and the mixing chamber on the first cylinder head; the total volume of the mixing chamber is the sum of the volume of the mixing chamber on the intermediate plate and the volume of the mixing chamber on the first cylinder head.

[0008] Optionally, the intermediate plate is further provided with a gas supplementing channel connected to the injection pipe, and the gas supplementing channel communicates with the mixing cavity of the intermediate plate.

[0009] Optionally, the central axis of the gas supplementing channel intersects with the central axis of the intermediate plate; or, the central axis of the gas supplementing channel neither intersects nor is parallel to the central axis of the intermediate plate, and the outlet direction of the gas supplementing channel follows the air flow direction of the primary exhaust in the mixing cavity of the intermediate plate.

[0010] Optionally, the central axis of the gas supplementing 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.

[0011] Optionally, the pump body further includes an intermediate flow channel, and the mixing cavity of the first cylinder head communicates with the mixing cavity of the intermediate plate through the intermediate flow channel.

[0012] Optionally, a first muffler is provided at one end of the first cylinder head facing away from the primary cylinder, and the first muffler and the first cylinder head enclose the mixing cavity of the first cylinder head, and / or, a second muffler is provided at one end of the second cylinder head facing away from the secondary cylinder.

[0013] Optionally, the ratio of the height to the outer diameter of the mixing cavity is 0.065 - 0.66.

[0014] Optionally, the ratio of the height to the outer diameter of the intermediate plate is 0.08 - 0.44.

[0015] Compared with the prior art, the compressor provided by the present invention has at least the following beneficial effects:

[0016] By setting the ratio of the total volume V2 of the mixing cavity to the displacement V1 of the compressor of the compressor provided by the present invention to be: 7 < V2 / V1 ≤ 12, the total volume of the mixing cavity is in an optimal state, so as to minimize gas loss and reduce gas flow pulsation; ultimately, the total heating capacity of the system is effectively improved without reducing the performance of the compressor.

[0017] In a further improvement, the compressor provided by the present invention exhausts gas to the mixing cavity of the intermediate plate and the mixing cavity of the first cylinder head through the primary cylinder at the same time, which can better stabilize the primary exhaust gas flow, reduce the loss of exhaust gas, and reduce gas pulsation.

[0018] In a further improvement, by directly providing the gas supplementing channel on the intermediate plate of the compressor provided by the present invention, the gas supplementing gas can be directly sprayed into the mixing cavity of the intermediate plate, thereby shortening the gas supplementing path, reducing the loss of the gas supplementing injection gas, and having no influence on the secondary suction. Description of the Drawings

[0019] 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:

[0020] Figure 1 It is a schematic structural diagram of a compressor provided for a preferred embodiment of the present invention, and the illustrated arrows indicate the refrigerant flow path;

[0021] Figure 2 It is a schematic structural diagram of an intermediate plate provided for a preferred embodiment of the present invention;

[0022] Figure 3 It shows the influence of the mixing chamber volume and the compressor displacement on the heating capacity of the system obtained from the test results of the present invention. The abscissa is the ratio of the mixing chamber volume to the compressor displacement, and the ordinate is the heating capacity of the system;

[0023] Figure 4 It shows the influence of the mixing chamber volume and the compressor displacement on the COP performance of the system obtained from the test results of the present invention. Among them, the abscissa is the ratio of the mixing chamber volume to the compressor displacement, and the ordinate is the compressor COP.

[0024] Among them,

Explanation of the reference numerals is as follows

[0025] 1 - housing, 2 - crankshaft, 3 - first - stage cylinder, 4 - second - stage cylinder, 5 - intermediate plate, 51 - exhaust hole of the intermediate plate, 52 - exhaust valve seat, 53 - boss, 54 - air - supplementing channel, 6 - first cylinder head, 7 - second cylinder head, 8 - mixing chamber, 9 - injection pipe, 10 - suction pipe, 11 - first muffler, 12 - second muffler, V1 - compressor displacement, V2 - total volume of the mixing chamber. Detailed implementation manners

[0026] To make the objectives, advantages and features of the present invention clearer, the following further describes the present invention in detail with reference to the drawings and specific embodiments. It should be noted that the drawings are all in a very simplified form and not drawn to scale, and are only used to conveniently and clearly assist in explaining the objectives of the embodiments of the present invention. In addition, the structures shown in the drawings are often part of the actual structures. In particular, the emphasis that each drawing needs to show is different, and sometimes different scales are used.

[0027] As used in the present invention, the singular forms "a", "an", "one" and "the" include plural referents, 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 construed as indicating or implying relative importance or implicitly specifying 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 two corresponding parts, which not only include the endpoints. In addition, as used in the present invention, "mounted", "connected", "coupled", and an element "disposed" on another element should be understood in a broad sense, generally only indicating that there is a connection, coupling, cooperation or transmission relationship between the two elements, and the two elements can be directly or indirectly connected, coupled, cooperated or transmitted through an intermediate element, rather than being construed as indicating or implying the spatial position relationship between the two elements, that is, an element can be in any position such as inside, outside, above, below or on one side of another element, unless the content clearly indicates otherwise. For those of ordinary skill in the art, the specific meanings of the above 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, and right are used relative to the exemplary embodiments as shown in the figures, the upward or upward direction is towards the top of the corresponding figure, and the downward or downward direction is towards the bottom of the corresponding figure.

[0028] The object of the present invention is to provide a compressor to solve the problems of large air flow pulsation and large gas loss existing in the compressor in the prior art. The compressor provided by the present invention is mainly applied to ultra-low temperature environments or ultra-high temperature environments and can better meet the heating or cooling requirements of the system. It should be noted that the compressor provided by the present invention is a vertical compressor or a horizontal compressor. The drawings only illustrate the case where the compressor is a vertical compressor, but this is not used as a limitation to the present invention. The following description is made with reference to the drawings.

[0029] As Figure 1 shown, an embodiment of the present invention relates to a compressor, specifically a two-stage enhanced enthalpy compressor, and includes: a housing 1 and a motor and a pump body disposed inside the housing 1. The motor is composed of a stator and a rotor disposed inside the stator. Here, since the motor is understandable to those skilled in the art, it is not shown in the drawings and will not be described in detail.

[0030] In addition, the pump body includes: a crankshaft 2, a first-stage cylinder 3, and a second-stage cylinder 4. Among them, the crankshaft 2 is sleeved inside the rotor of the motor, the second-stage cylinder 4, and the first-stage cylinder 3. When the compressor works, after the stator of the motor is electrified and starts, the rotor rotates, the rotor drives the crankshaft 2 to rotate, and the rotation of the crankshaft 2 drives the rolling pistons in the first-stage cylinder 3 and the second-stage cylinder 4 to rotate eccentrically to do work. In this embodiment, the first-stage cylinder 3 is on the side away from the motor, while the second-stage cylinder 4 is on the side close to the motor. In other embodiments, the first-stage cylinder 3 is on the side close to the motor, and the second-stage cylinder 4 is on the side away from the motor. The pump body further includes an intermediate plate 5, a first cylinder head 6, and a second cylinder head 7. The intermediate plate 5 is located between the first-stage cylinder 3 and the second-stage cylinder 4. The first cylinder head 6 is located at one end of the first-stage cylinder 3 facing away from the second-stage cylinder 4. The second cylinder head 7 is located at one end of the second-stage cylinder 4 facing away from the first-stage cylinder 3.

[0031] The pump body further includes a mixing chamber 8 and an injection pipe 9. The mixing chamber 8 is arranged inside the housing 1, and the injection pipe 9 passes through the housing 1 and extends to the inside of the housing 1 to be connected with the mixing chamber 8. It should be noted that the mixing chamber 8 can be arranged only on the first cylinder head 6, or only on the intermediate plate 5, or the mixing chamber 8 is arranged on both the first cylinder head 6 and the intermediate plate 5 at the same time. The mixing chamber 8 is beneficial to reducing the pulsation influence of the first-stage exhaust, the second-stage suction, and the air flow injected into the compressor. Thus, the refrigerant compressed by the first-stage cylinder 3 is discharged into the mixing chamber 8, and then inhaled by the second-stage cylinder 4 from the mixing chamber 8. At the same time, the injection pipe 9 is used to inject supplementary gas into the mixing chamber 8 to improve the heating capacity of the system.

[0032] And it is found through research that for a two-stage enthalpy-increasing compressor, the volume of the mixing chamber 8 is not the larger the better. Through a large number of experimental studies, the present invention finds that when the ratio of the total volume V2 of the mixing chamber 8 to the displacement V1 of the compressor is set at: 7 < V2:V1 ≤ 12, the total volume of the mixing chamber 8 can be in an optimal state, so as to minimize gas loss, reduce air flow pulsation, ultimately effectively improve the total heating capacity of the system, and at the same time not reduce the performance of the compressor. In the present invention, the total volume V2 of the mixing chamber 8 is adjusted according to the displacement V1 of the compressor, which can not only reduce the pulsation influence of the first-stage exhaust pulsation, the second-stage suction pulsation, and the supplementary gas injected into the mixing chamber 8, but also minimize the compressor input as much as possible, so that the performance of the compressor can be guaranteed.

[0033] Further preferably, 7.1 ≤ V2 / V1 ≤ 12. For example, optionally, the value of V2 / V1 is 7.1, 8, 9, 10, 11, or 12; so that the heating performance of the compressor and the overall performance of the compressor are the best.

[0034] Preferably, as Figure 1As shown, mixing chambers 8 are provided on both the intermediate plate 5 and the first cylinder head 6. The mixing chamber 8 of the intermediate plate 5 and the mixing chamber 8 of the first cylinder head 6 are both connected to the first-stage cylinder 3. The first-stage cylinder 3 is configured to exhaust gas to the mixing chamber 8 of the intermediate plate 5 and the mixing chamber 8 of the first cylinder head 6 simultaneously, that is, the first-stage cylinder 3 exhausts gas up and down simultaneously. After being compressed by the first-stage cylinder 3, the refrigerant gas path is divided into two paths. One path is discharged into the mixing chamber 8 of the first cylinder head 6, and the other path is discharged into the mixing chamber 8 of the intermediate plate 5. The first-stage cylinder 3 exhausting gas up and down simultaneously can effectively improve the volumetric efficiency of the compressor and increase the heating capacity of the system. At this time, the total volume of the mixing chamber 8 is the sum of the volume of the mixing chamber 8 of the intermediate plate 5 and the volume of the mixing chamber 8 of the first cylinder head 6.

[0035] After the mixing chambers 8 are provided on the intermediate plate 5 and the first cylinder head 6 simultaneously, it is equivalent to increasing the mixing chamber 8, which is beneficial to stabilizing the first-stage exhaust gas flow, reducing gas pulsation, and further reducing the losses caused by gas pulsation. If the mixing chamber 8 of the intermediate plate 5 is directly enlarged, 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, thereby increasing the force on the crankshaft 2, which is disadvantageous. Therefore, in this embodiment, increasing the height of the intermediate plate 5 is not considered, but adding a mixing chamber 8 at the first cylinder head 6 is selected, which can not only avoid increasing the force on the crankshaft 2 but also stabilize the first-stage exhaust gas flow.

[0036] In addition, the mixing chamber 8 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 simultaneously. Therefore, the mixing chamber 8 of the intermediate plate 5 can reduce the frictional resistance of the first-stage exhaust gas flow to the second-stage suction, thereby reducing the loss of the first-stage exhaust gas. On the other hand, when the first-stage cylinder 3 exhausts gas up and down simultaneously, the gas discharged into the mixing chamber 8 of the first cylinder head 6 can become more stable in the mixing chamber 8 of the first cylinder head 6 before entering the mixing chamber 8 of the intermediate plate 5. Compared with the first-stage cylinder 3 directly discharging all the gas into the mixing chamber 8 of the intermediate plate 5, the first-stage exhaust gas flow is stabilized, the gas pulsation in the mixing chamber 8 of the intermediate plate 5 is reduced, and thus the losses caused by gas pulsation are reduced.

[0037] It should also be noted that although it is described as the mixing chamber 8 of the first cylinder head 6 above, the mixing chamber 8 of the first cylinder head 6 can be provided inside the first cylinder head 6, outside the first cylinder head 6, or both inside and outside the first cylinder head 6 simultaneously.

[0038] It is also found that if the air supplement gas is directly arranged at the secondary suction of the secondary cylinder 4, losses may be caused to the secondary suction; if the air supplement gas is directly arranged at the mixing chamber 8 of the first cylinder head 6, since the gas in the mixing chamber 8 of the first cylinder head 6 still needs to converge into the mixing chamber 8 of the intermediate plate 5 before being inhaled by the secondary cylinder 4, the air supplement path is too long at this time, which is likely to cause losses of the air supplement injection gas. Therefore, in this embodiment, the air supplement gas is preferably directly arranged in the mixing chamber 8 of the intermediate plate 5 closest to the secondary suction, which neither affects the secondary suction nor causes losses of the air supplement injection gas.

[0039] More specifically, as Figure 1 and Figure 2 shown, preferably, the intermediate plate 5 is further provided with an air supplement channel 54 connected to the injection pipe 9, and the air supplement channel 54 is communicated with the mixing chamber 8 of the intermediate plate 5. The air supplement channel 54 is a through-hole structure and is opened on the side surface of the intermediate plate 5. And the air supplement channel 54 is preferably a circular hole. For the convenience of assembly, the air supplement channel 54 is usually arranged as a stepped hole, and the injection pipe 9 is connected to the large-diameter hole close to the outside in the air supplement channel 54.

[0040] Thus, when the compressor provided in this embodiment works, the refrigerant enters the primary cylinder 3 through the suction pipe 10. After being compressed by the primary cylinder 3, the gas path is divided into two paths. One path is discharged into the mixing chamber 8 of the first cylinder head 6, and the other path is discharged into the mixing chamber 8 of the intermediate plate 5. The gas discharged into the mixing chamber 8 of the intermediate plate 5 is mixed with the air supplement gas injected into the mixing chamber 8 of the intermediate plate 5 by the injection pipe 9 to form a mixed gas. After the gas discharged into the mixing chamber 8 of the first cylinder head 6 becomes stable, it then enters the mixing chamber 8 of the intermediate plate 5 and is inhaled by the secondary cylinder 4 together with the mixed gas after being mixed again.

[0041] Furthermore, from the perspective of the first-stage exhaust flow resistance, the larger the mixing chamber 8 is, the smaller the first-stage exhaust resistance is, and the smaller the disturbance of the gas discharged into the mixing chamber 8 from the first stage to the gas in the mixing chamber 8 in the intermediate plate 5 is, and the smaller the resistance of the second-stage suction is. At the same time, since the mixing chamber 8 is also provided with a gas replenishing channel 54, the larger the mixing chamber 8 is, the smaller the disturbance of the injected gas to the first-stage exhaust and the second-stage suction is, that is, the smaller the suction and exhaust loss of the compressor is, the larger the heating capacity is, and the better the performance is. However, after the mixing chamber 8 is enlarged, it will cause an increase in the friction surface of the compressor, an increase in the heat exchange area, and an increase in the process difficulty. And since the components of the compressor are all molded, the rough machining process is minimized as much as possible. Then, the intermediate plate 5 and the first cylinder head 6 close to the first-stage cylinder 3 are both designed with a mixing chamber 8, so the difficulty of pouring and demolding the components is increased. Therefore, when designing, the diameter of the components with the mixing chamber 8 is generally set to be the same as that of other components. The mixing chamber 8 is designed and changed by the height of the component. A more reasonable design is that the ratio of the height to the outer diameter of the mixing chamber 8 is 0.065 to 0.66, which can be the ratio of the height of the mixing chamber 8 at the first cylinder head 6 to the outer diameter of this mixing chamber 8, or the ratio of the height of the mixing chamber 8 at the intermediate plate 5 to the outer diameter of this mixing chamber 8. Therefore, there are design upper limits for the heights of both the first cylinder head 6 and the intermediate plate 5 close to the first-stage cylinder 3. In addition, the height of the intermediate plate 5 directly affects the force on the crankshaft 2 of the compressor. The higher the height of the intermediate plate 5 is, the larger the distance between the two cylinders is, the longer the force arm of the gas force acting on the crankshaft 2 is, and the worse the force on the crankshaft 2 is, and the power consumption of the compressor increases. Therefore, there is also an upper limit for the total height of the intermediate plate 5. A more reasonable design is that the ratio of the height to the outer diameter of the intermediate plate 5 is 0.08 to 0.44. Therefore, when designing the volume of the mixing chamber 8 and the displacement of the compressor, not only the heating capacity should be considered, but also the force on the crankshaft 2 and the process feasibility should be considered simultaneously.

[0042] As Figure 2 shown, in one way, the intermediate plate 5 is provided with an exhaust hole 51. The mixing chamber 8 of the intermediate plate 5 is communicated with the first-stage cylinder 3 through the exhaust hole 51, and an exhaust valve seat 52 is provided at the exhaust hole 51. An exhaust valve plate can be arranged on the exhaust valve seat 52. One end of the exhaust valve plate is fixed on the exhaust valve seat 52, and the other end is arranged at the exhaust hole 51. During exhaust, the exhaust valve plate is opened, and the first-stage cylinder 3 exhausts gas to the mixing chamber 8 of the intermediate plate 5 through the exhaust hole 51.

[0043] And when the mixing chamber 8 is arranged on the first cylinder head 6, the pump body further includes an intermediate flow channel. The mixing chamber 8 of the first cylinder head 6 is communicated with the mixing chamber 8 of the intermediate plate 5 through the intermediate flow channel, so that a path of gas discharged into the mixing chamber 8 of the first cylinder head 6 then enters the mixing chamber 8 of the intermediate plate 5 through the intermediate flow channel on the pump body.

[0044] As Figure 1As shown, at one end of the first cylinder head 6 away from the first-stage cylinder 3, a first muffler 12 is provided. Preferably, the first muffler 12 and the first cylinder head 6 directly enclose a mixing chamber 8 at the lower part of the first cylinder head 6. Of course, it is not limited to this in practice. Further, the intermediate flow channel includes through holes on the first cylinder head 6, through holes on the cylinder block of the first-stage cylinder 3, and through holes on the intermediate plate 5 that are axially connected in sequence.

[0045] Generally, at one end of the second cylinder head 7 away from the second-stage cylinder 4, a second muffler 13 is provided. The gas compressed by the second-stage cylinder 4 is directly discharged into the second muffler 13 through the air flow channel on the second cylinder head 7, and then discharged into the housing 1 through the second muffler 13.

[0046] Returning to the reference Figure 2 , preferably, a mixing chamber 8 with a circular cross-section is provided inside the intermediate plate 5, and an air supplement channel 54 is provided on the outer wall surface of the mixing chamber 8 of the intermediate plate 5. In one way, the central axis of the air supplement channel 54 intersects with the central axis of the intermediate plate 5. In another way, the central axis of the air supplement channel 54 neither intersects nor is parallel to the central axis of the intermediate plate 5. When the central axis of the air supplement channel 54 intersects with the central axis of the intermediate plate 5, the air supplement channel 54 is arranged in a horizontal direction, an obliquely upward direction, or an obliquely downward direction. Similarly, when the central axis of the air supplement channel 54 neither intersects nor is parallel to the central axis of the intermediate plate 5, the air supplement channel 54 is arranged in a horizontal direction, an obliquely upward direction, or an obliquely downward direction. The horizontal direction corresponds to the central axis of the air supplement channel 54 being parallel to the cross-sectional direction of the intermediate plate 5, and the cross-section of the intermediate plate 5 is perpendicular to the central axis of the intermediate plate 5.

[0047] Particularly, when the central axis of the air supplement channel 54 neither intersects nor is parallel to the central axis of the intermediate plate 5, the included angle between the central axis of the air supplement channel 54 and the radial direction of the mixing chamber 8 of the intermediate plate 5 is less than or equal to 90°. Preferably, when the central axis of the air supplement channel 54 neither intersects nor is parallel to the central axis of the intermediate plate 5, the outlet direction of the air supplement channel 54 follows the air flow direction of the first-stage exhaust in the mixing chamber 8 inside the intermediate plate 5, which can minimize the resistance of the injected air supplement gas as much as possible, and at the same time reduce the influence on the first-stage exhaust in the mixing chamber 8 inside the intermediate plate 5, reduce air flow loss, and reduce the disturbance to the first-stage exhaust.

[0048] In addition, the intermediate plate 5 can be a circular structure or a non-circular structure. For example, as Figure 1 shown, the intermediate plate 5 is a circular structure as a whole, or, as Figure 2 shown, the intermediate plate 5 adopts a non-circular structure, and a boss 53 is provided at the corresponding position on the outer wall surface of the intermediate plate 5, and the air supplement channel 54 is opened on the boss 53. Of course, the intermediate plate 5 here is only used to provide a further understanding of the present invention and does not constitute an improper limitation to the present invention.

[0049] Combined with the test results, the beneficial effects presented by the compressor provided by the present invention in improving the heating capacity of the system and ensuring the performance of the compressor will be further described below.

[0050] Figure 3 The influence of the ratio of the volume of the mixing chamber to the displacement of the compressor on the heating capacity of the system is given. In Figure 3 , the ambient temperature during the operation of the compressor is -12°C, and it can be seen from the change of the curve that when the ratio of the total volume V2 of the mixing chamber 8 to the displacement V1 of the compressor is less than 7, the change range of the curve slope is relatively large, which indicates that there are obvious losses in each part of the air flow and the pulsation is large, so the loss of the heating capacity is large; while when the ratio of the total volume V2 of the mixing chamber 8 to the displacement V1 of the compressor is greater than 7 and less than or equal to 12, the change range of the curve slope is very small, indicating that the air flow pulsation is small, the overall loss of the air flow is small, the heating capacity of the compressor is relatively stable, and the overall heating capacity of the heat pump system of the compressor is improved. Therefore, when 7 < V2 / V1 ≤ 12, the compressor is in the optimal state. At the same time, combined with Figure 4 shown, the COP performance of the compressor first increases and then decreases with the increase of the ratio of the volume of the mixing chamber to the displacement of the compressor. Once the ratio exceeds 12, the COP shows an obvious downward trend. Therefore, it is best that V2 / V1 does not exceed 12.

[0051] On the other hand, from the test results of the actual installation, it can be seen that after the total volume V2 of the mixing chamber 8 is increased from 6 times the displacement V1 of the compressor to 9 times (i.e., V2 / V1 = 9), the increase in the heating capacity is shown in Table 1.

[0052] Table 1: Variation of the total heating capacity under different working conditions

[0053]

[0054] Where: Te is the evaporation temperature and Tc is the condensation temperature.

[0055] According to Table 1, when 7 < V2 / V1 ≤ 12, the total heating capacity of the system increases at different evaporation temperatures, and the lower the evaporation temperature (ambient temperature), the greater the increase in the heating capacity.

[0056] In summary, for the compressor provided by the present invention, the ratio of the total volume V2 of the mixing chamber 8 to the displacement V1 of the compressor is set as: 7 < V2 / V1 ≤ 12, so that the total volume of the mixing chamber 8 is in an optimal state, minimizing gas loss, reducing gas pulsation, enhancing the heating capacity of the system, and not degrading the performance of the compressor. On this basis, the compressor provided by the present invention simultaneously discharges air up and down through the first-stage cylinder 3, which can better stabilize the first-stage exhaust air flow, reduce gas pulsation, and reduce the loss caused by gas pulsation. Further, by directly opening the gas replenishing channel 51 on the intermediate plate 5, the compressor provided by the present invention enables the replenishing gas to be directly injected into the mixing chamber 8 of the intermediate plate 5, thereby shortening the gas replenishing path, reducing the loss of the replenishing injection gas, and having no impact on the second-stage suction.

[0057] The above description is only for the 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 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 compressor, characterized in that, include: An outer shell and a pump body arranged in the outer shell; the pump body includes a primary cylinder, a secondary cylinder, a mixing chamber and an injection pipe; an intermediate plate is provided between the primary cylinder and the secondary cylinder; the mixing chamber is connected to the injection pipe, and the injection pipe is used to inject supplementary gas into the mixing chamber; and the refrigerant compressed by the primary cylinder is discharged into the mixing chamber, and then sucked into the secondary cylinder by the mixing chamber; wherein: the displacement of the compressor is V1, the total volume of the mixing chamber is V2, 7<V2 / V1≤12.

2. The compressor according to claim 1, characterized in that, 7.1≤V2 / V1≤12.

3. The compressor according to claim 1 or 2, characterized in that, A first cylinder head is provided at one end of the first-stage cylinder facing away from the middle plate, and a second cylinder head is provided at one end of the second-stage cylinder facing away from the middle plate. Both the middle plate and the first cylinder head are provided with the mixing chamber; the first-stage cylinder is configured to exhaust gas to the mixing chamber of the middle plate and the mixing chamber of the first cylinder head at the same time; the total volume of the mixing chamber is the sum of the volume of the mixing chamber of the middle plate and the volume of the mixing chamber of the first cylinder head.

4. The compressor according to claim 3, characterized in that, The middle plate is also provided with an air supply channel connected to the injection pipe, and the air supply channel is communicated with the mixing chamber of the middle plate.

5. The compressor according to claim 4, wherein The central axis of the air supplement channel intersects with the central axis of the middle plate; or, the central axis of the air supplement channel does not intersect or is not parallel to the central axis of the middle plate, and the outlet direction of the air supplement channel follows the airflow direction of the primary exhaust gas in the mixing chamber in the middle plate.

6. The compressor according to claim 5, characterized in that, The central axis of the air supplement channel is arranged parallel to the cross-sectional direction of the middle plate, and the cross-sectional direction is perpendicular to the central axis of the middle plate.

7. The compressor according to claim 3, wherein The pump body further comprises an intermediate flow passage, through which the mixing chamber of the first cylinder head is communicated with the mixing chamber of the intermediate plate.

8. The compressor according to claim 7, characterized in that, A first muffler is arranged at one end of the first cylinder head away from the primary cylinder, and the first muffler and the first cylinder head form a mixing chamber of the first cylinder head, and / or a second muffler is arranged at one end of the second cylinder head away from the secondary cylinder.

9. The compressor according to claim 1 or 2, characterized in that The ratio of the height to the outer diameter of the mixing chamber is 0.065-0.

66.

10. The compressor according to claim 9, characterized in that, The ratio of the height to the outer diameter of the intermediate plate is 0.08 to 0.44.

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