CN113931841A

CN113931841A - A multi-cylinder rotary compressor

Info

Publication number: CN113931841A
Application number: CN202010604569.4A
Authority: CN
Inventors: 熊俊; 张利; 周易; 徐沈平
Original assignee: Nanchang Hichly Electrical Appliance Co ltd; Shanghai Highly Electrical Appliances Co Ltd
Current assignee: Nanchang Hichly Electrical Appliance Co ltd; Shanghai Highly Electrical Appliances Co Ltd
Priority date: 2020-06-29
Filing date: 2020-06-29
Publication date: 2022-01-14

Abstract

The invention provides a multi-cylinder rotary compressor, comprising a crankshaft and a plurality of cylinders; a plurality of eccentric parts are arranged on the axial direction of the crankshaft, and the eccentric parts are arranged in a one-to-one correspondence with the cylinders, and two adjacent eccentric parts are provided Arranged at 180°±A°; each cylinder has a refrigerant circulation part for sucking and discharging refrigerant, and the refrigerant circulation part includes a suction port and an exhaust port. On the cross section of each cylinder, the axis of the suction port Symmetrical with the axis of the exhaust port with respect to a preset line, the refrigerant circulation part has a direction vector passing through the preset line, the direction vector corresponding to the first cylinder is in the same direction as the direction vector corresponding to the second cylinder, and the direction corresponding to the third cylinder is the same. The vector is in the same direction as the direction vector corresponding to the fourth cylinder, and the direction vector corresponding to the second cylinder is opposite to the direction vector corresponding to the third cylinder; the present application reduces the crankshaft force of the multi-cylinder compressor and improves the reliability of the compressor .

Description

Rotary compressor with multiple cylinders

Technical Field

The invention relates to the technical field of compressors, in particular to a rotary compressor with multiple cylinders.

Background

The prior rotary compressor is developed towards the direction of high capacity, and the capacity of the cylinder cannot be further increased due to the limitation of the structural size of the whole machine. Therefore, a multi-cylinder system is generally required.

In a high capacity rotary compressor composed of a plurality of cylinders, the stress on the crankshaft is large. In particular, as the displacement of the compressor tends to be larger, the gas force applied to the crankshaft gradually increases as the displacement increases. The risk of bending deformation of the crankshaft is increased, and the bending of the crankshaft can have adverse effects on the fit clearance of all parts of the pump body of the compressor, so that the reliability and the performance of the compressor are reduced. Therefore, when the displacement of the compressor is continuously increased, the stress condition of the crankshaft needs to be optimized, and the reliability of the compressor is ensured; the torque fluctuation of the crankshaft is required to be as small as possible, so that the vibration and the noise of the compressor are small.

Disclosure of Invention

In view of this, the present invention provides a multi-cylinder rotary compressor, which effectively reduces the resultant force of the gas applied to the crankshaft of the compressor, and improves the reliability of the compressor.

According to an aspect of the present invention, there is provided a multi-cylinder rotary compressor including a crankshaft and a plurality of cylinders;

a plurality of eccentric parts are arranged on the axial direction of the crankshaft, the eccentric parts and the cylinders are arranged in a one-to-one correspondence mode, two adjacent eccentric parts are arranged in an angle of 180 degrees +/-A degrees, and the angle of A degrees is more than or equal to 0 and less than or equal to 45 degrees;

the plurality of cylinders at least comprise a first cylinder, a second cylinder, a third cylinder and a fourth cylinder which are sequentially arranged along the axial direction of the crankshaft;

each cylinder is provided with a refrigerant circulating part for sucking and discharging refrigerants, the refrigerant circulating part comprises an air suction port and an air exhaust port, a preset line is determined by the axis of the air suction port and the axis of the air exhaust port on the cross section of each cylinder, the refrigerant circulating part is provided with a direction vector passing through the preset line, the direction vector corresponding to the first cylinder is the same as the direction vector corresponding to the second cylinder, the direction vector corresponding to the third cylinder is the same as the direction vector corresponding to the fourth cylinder, the direction vector corresponding to the second cylinder and the direction vector corresponding to the third cylinder form an included angle with a value range of 135-225 degrees, and the cross section of each cylinder is a section perpendicular to the height direction of the cylinder.

Preferably, the compressor further comprises an upper cylinder cover and a lower cylinder cover, and the cylinders are arranged between the upper cylinder cover and the lower cylinder cover; the axis of the air suction port of the first cylinder is perpendicular to the upper surface of the first cylinder, the axis of the air suction port of the second cylinder is perpendicular to the plane of the air suction port of the fourth cylinder, and the upper surface of the first cylinder is the surface of the first cylinder close to the upper cylinder cover.

Preferably, the intake port of the first cylinder and the intake port of the third cylinder have a phase difference of 180 °, the intake port of the second cylinder and the intake port of the fourth cylinder have a phase difference of 180 °, and the phase difference between the intake port of the first cylinder and the intake port of the second cylinder is 0 °.

Preferably, all be equipped with the blade groove on the cylinder in order to hold the blade and slide, the blade that first cylinder corresponds with contained angle between the blade that the second cylinder corresponds is 0, the blade that the third cylinder corresponds with contained angle between the blade that the fourth cylinder corresponds is 0, the blade that the second cylinder corresponds with contained angle between the blade that the third cylinder corresponds is 180.

Preferably, each eccentric part is sleeved with a piston, the piston is matched with the blade to divide the inner space of the cylinder into a suction cavity communicated with the suction port and an exhaust cavity communicated with the exhaust port; the air suction cavity of the first cylinder and the air suction cavity of the fourth cylinder are point-symmetrical about the center of the first cylinder, and the air suction cavity of the second cylinder and the air suction cavity of the third cylinder are point-symmetrical about the center of the second cylinder.

Preferably, the first cylinder and the fourth cylinder have the same volume of intake chamber and the same volume of exhaust chamber, and the second cylinder and the third cylinder have the same volume of intake chamber and the same volume of exhaust chamber.

Preferably, the air suction port is a circular hole, and a projection of the air suction port on a cross section of the cylinder is symmetrical about an axis of the air suction port.

Preferably, the cylinders each have a hollow annular body, the annular body of the second cylinder has a radial width equal to the radial width of the annular body of the third cylinder, the annular body of the first cylinder has a radial width equal to the radial width of the annular body of the fourth cylinder, and the annular body of the second cylinder has a radial width greater than the radial width of the annular body of the first cylinder.

Preferably, the plurality of cylinders are four cylinders, four eccentric portions are arranged on the crankshaft, and the four eccentric portions are respectively a first eccentric portion, a second eccentric portion, a third eccentric portion and a fourth eccentric portion which are sequentially arranged along the axial direction of the crankshaft, the first eccentric portion is located in the first cylinder, the second eccentric portion is located in the second cylinder, the third eccentric portion is located in the third cylinder, and the fourth eccentric portion is located in the fourth cylinder.

Preferably, the compressor further comprises a first liquid storage device and a second liquid storage device, the air suction port of the first cylinder and the air suction port of the second cylinder are both connected with the first liquid storage device, and the air suction port of the third cylinder and the air suction port of the fourth cylinder are both connected with the second liquid storage device.

Preferably, the compressor further comprises a reservoir, and the air suction port of the first cylinder, the air suction port of the second cylinder, the air suction port of the third cylinder and the air suction port of the fourth cylinder are all connected with the reservoir.

Compared with the prior art, the invention has the beneficial effects that:

the multi-cylinder rotary compressor provided by the invention can effectively reduce the resultant force of gas borne by the crankshaft of the compressor, reduce the bending degree of the crankshaft, reduce the abrasion of the crankshaft and improve the operation reliability of the compressor on the premise of realizing large discharge capacity and improving the refrigeration capacity of the compressor; moreover, the torque fluctuation is smooth, and the running noise is low.

Drawings

The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the invention and together with the description, serve to explain the principles of the invention. It is obvious that the drawings in the following description are only some embodiments of the invention, and that for a person skilled in the art, other drawings can be derived from them without inventive effort.

Fig. 1 is a sectional view showing a structure of a double-cylinder rotary compressor in the prior art;

FIG. 2 is a schematic structural view of the upper cylinder of FIG. 1;

FIG. 3 is a schematic view of the structure of the lower cylinder of FIG. 1;

fig. 4 is a sectional view showing the structure of a multi-cylinder rotary compressor according to an embodiment of the present invention;

FIG. 5 is a structural cross-sectional view of the crankshaft of FIG. 4;

FIG. 6 is a schematic view of the first cylinder of FIG. 4;

FIG. 7 is a schematic diagram of the second cylinder of FIG. 4;

FIG. 8 is a schematic diagram of the third cylinder of FIG. 4;

FIG. 9 is a schematic diagram of the fourth cylinder of FIG. 4;

FIG. 10 is a graph illustrating a comparison of crankshaft stress for a single cylinder rotary compressor and a dual cylinder rotary compressor of the prior art;

FIG. 11 is a schematic diagram of crankshaft torque comparison of a single cylinder rotary compressor and a dual cylinder rotary compressor of the prior art;

FIG. 12 is a schematic diagram of a crankshaft stress of a multi-cylinder rotary compressor according to an embodiment of the present invention;

fig. 13 is a schematic diagram of crankshaft torque of a multi-cylinder rotary compressor according to an embodiment of the present invention.

Detailed Description

Example embodiments will now be described more fully with reference to the accompanying drawings. Example embodiments may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the concept of example embodiments to those skilled in the art. The described features, structures, or characteristics may be combined in any suitable manner in one or more embodiments. In the following description, numerous specific details are provided to give a thorough understanding of embodiments of the disclosure. One skilled in the relevant art will recognize, however, that the subject matter of the present disclosure can be practiced without one or more of the specific details, or with other methods, materials, devices, etc. In other instances, well-known technical solutions have not been shown or described in detail to avoid obscuring aspects of the present disclosure. The same reference numerals in the drawings denote the same or similar structures, and thus their detailed description will be omitted.

The terms "a," "an," "the," "said," and "at least one" are used to indicate the presence of one or more elements/components/parts/etc.; the terms "comprising," "having," and "providing" are intended to be inclusive and mean that there may be additional elements/components/etc. other than the listed elements/components/etc.

The prior art rotary compressor mainly uses a single cylinder and double cylinders. The single-cylinder rotary compressor is provided with a cylinder, and the cylinder is arranged between an upper cylinder cover and a lower cylinder cover. The air suction port of the air cylinder is connected with the liquid storage device. Fig. 1 is a schematic view of a twin-cylinder rotary compressor in the prior art. As shown in fig. 1, the double cylinder compressor includes a housing 101, an upper cylinder head 102, an upper cylinder 103, an intermediate plate 104, a lower cylinder 105, a lower cylinder head 106, and a crankshaft 107, wherein the intermediate plate 104 is located between the upper cylinder 103 and the lower cylinder 105, and the upper cylinder 103 and the lower cylinder 105 are both disposed between the upper cylinder head 102 and the lower cylinder head 106.

Fig. 2 and 3 are schematic structural views of the upper cylinder 103 and the lower cylinder 105 in fig. 1, respectively. As shown in fig. 2, the inner space of the upper cylinder 103 is partitioned into a first suction chamber 203 and a first discharge chamber 204 by the first vane 201 and the first piston 202. As shown in fig. 3, the inner space of the lower cylinder 105 is partitioned into a second suction chamber 303 and a second discharge chamber 304 by a second vane 301 and a second piston 302. Crankshaft 107 rotates first piston 202 and second piston 302, respectively.

The upper cylinder 103 has a first suction port 205, the lower cylinder 105 has a second suction port 305, and the first and

second suction ports

205 and 305 are located on the same side, i.e. the axis of the first suction port 205 and the axis of the second suction port 305 each form an angle of 0 ° between their projections onto the upper surface of the upper cylinder. The upper surface of the upper cylinder is a side surface thereof close to the upper cylinder head 102.

When the center point of the first piston 202 inside the upper cylinder 103 rotates by an angle θ, the center point of the second piston 302 inside the lower cylinder 105 rotates by an angle (θ +180 °), and at this time, the volumes of the first suction chamber 203 and the second suction chamber 303 are always inconsistent, and similarly, the volumes of the first discharge chamber 204 and the second discharge chamber 304 are also always inconsistent. For the compressors with the same structure design, if the number of cylinders is simply increased in order to increase the displacement of the compressor, for example, the crankshaft of the four-cylinder compressor designed by the above-mentioned double-cylinder rotary compressor structure is stressed twice as much as the crankshaft of the above-mentioned double-cylinder rotary compressor. This will make the risk that the bent axle warp obviously improve, and the bent axle will produce harmful effects to each part fit clearance of compressor pump body, lead to the reliability that can't guarantee large discharge capacity compressor work. The direction of the arrows in fig. 2 and 3 is the flow direction of the refrigerant gas inside the cylinder.

Therefore, the invention discloses a multi-cylinder rotary compressor, which comprises an upper cylinder cover, a lower cylinder cover, a crankshaft and a plurality of cylinders. The plurality of cylinders are all arranged between the upper cylinder cover and the lower cylinder cover. The axial of the crankshaft is provided with a plurality of eccentric parts, the eccentric parts and the cylinders are arranged in a one-to-one correspondence manner, and two adjacent eccentric parts are arranged in an angle of 180 degrees +/-A degrees, wherein the angle of A degrees is more than or equal to 0 degrees and less than or equal to 45 degrees. That is, two adjacent eccentric portions are arranged at any angle ranging from 135 ° to 225 °. Preferably, when a is 0 °, two adjacent eccentric portions are symmetrically distributed at 180 °. In the following embodiments, two adjacent eccentric portions are symmetrically distributed at 180 °, as an example, unless otherwise specified. Wherein, the number of the cylinders is a multiple of 4. That is, the cylinder is formed by at least one cylinder group, and each cylinder group comprises four cylinders which are sequentially arranged along the axial direction of the crankshaft and are respectively a first cylinder, a second cylinder, a third cylinder and a fourth cylinder.

Each cylinder has a refrigerant circulating portion for sucking and discharging a refrigerant. The refrigerant circulating part includes an air suction port and an air discharge port. The air suction port is used for sucking the refrigerant, and the air exhaust port is used for exhausting the refrigerant. In each of the cylinders, the axis of the intake port and the axis of the exhaust port define a predetermined line in cross section. Wherein a projection of the axis of the intake port on the cylinder cross section and a projection of the axis of the exhaust port on the cylinder cross section may be symmetrical about the preset line. The air suction port is a circular hole, and the projection of the air suction port on the cross section of the cylinder can be symmetrical about the axis of the air suction port; the projection of the exhaust port on the cross section of the cylinder may be symmetrical with respect to the axis of the exhaust port. The cross section of the cylinder is a section of the cylinder perpendicular to its own height direction.

Each cylinder is provided with a blade groove for accommodating the blade to slide, each eccentric part is sleeved with a piston, the piston is matched with the blade, and the inner space of each cylinder is divided into a suction cavity communicated with the suction port and an exhaust cavity communicated with the exhaust port.

The refrigerant circulation part is provided with a direction vector passing through the preset line. Therefore, each cylinder has a corresponding direction vector. The direction vector corresponding to the first cylinder is the same as the direction vector corresponding to the second cylinder. The direction vector corresponding to the third cylinder is in the same direction as the direction vector corresponding to the fourth cylinder. The direction vector corresponding to the second cylinder and the direction vector corresponding to the third cylinder form an included angle with the value range of 135-225 degrees.

The volumes of the air suction cavity and the air exhaust cavity in the first cylinder and the fourth cylinder are respectively equal. This causes the gas in the first cylinder and the gas in the fourth cylinder to act on the crankshaft in equal and opposite directions. Therefore, the resultant force of the forces of the gas in the first cylinder and the fourth cylinder on the crankshaft is zero. Similarly, the resultant of the forces of the gases in the second and third cylinders on the crankshaft is also zero. Therefore, the resultant force of the acting force of each cylinder group on the crankshaft is always zero, so that the stress condition of the crankshaft is improved, and the bending deformation degree of the crankshaft is reduced.

Because the direction vector corresponding to the first cylinder is the same as the direction vector corresponding to the second cylinder, and the eccentric parts in the first cylinder and the second cylinder are symmetrical by 180 degrees, the resultant torque of the gas in the first cylinder and the gas in the second cylinder is consistent with that of the double-cylinder compressor in the prior art. Similarly, the combined torque of the gas in the third cylinder and the gas in the fourth cylinder is also consistent with the prior art two-cylinder compressor. Similarly, the combined torque of the gas in the third cylinder and the gas in the fourth cylinder is also consistent with the prior art two-cylinder compressor. And the resultant torque of the gas in the first cylinder and the gas in the second cylinder in each cylinder group is equal to the resultant torque of the gas in the third cylinder and the gas in the fourth cylinder in size and direction. This makes the compressor that this application provided under the prerequisite of discharge capacity increase, cylinder quantity increase, moment fluctuation and conventional double-cylinder compressor keep unanimous, and is comparatively gentle, has guaranteed that compressor running noise is lower.

Fig. 4 is a schematic structural diagram of a compressor according to an embodiment of the present invention. As shown in fig. 4, in the present embodiment, the compressor includes a crankshaft 408 and four cylinders, namely, a first cylinder 401, a second cylinder 402, a third cylinder 403, and a fourth cylinder 404, which are sequentially arranged along the axial direction of the crankshaft 408. The compressor further includes a housing 405, an upper cylinder head 406, and a lower cylinder head 407. Four cylinders are provided between the upper head 406 and the lower head 407. Each cylinder has a hollow annular body.

As shown in fig. 5, the crankshaft 408 is provided with four eccentric portions, namely, a first eccentric portion 501, a second eccentric portion 502, a third eccentric portion 503, and a fourth eccentric portion 504, which are provided in this order in the axial direction of the crankshaft 408. Two adjacent eccentric parts are symmetrically arranged at 180 degrees. The first eccentric portion 501 is located in the first cylinder 401, the second eccentric portion 502 is located in the second cylinder 402, the third eccentric portion 503 is located in the third cylinder 403, and the fourth eccentric portion 504 is located in the fourth cylinder 404.

As shown in fig. 6, the first cylinder 401 has a first refrigerant circulating part 601 and a first annular body 602, and is provided with a first vane groove for receiving the first vane 603 to slide. The first refrigerant circulating portion 601 includes a first suction port 604 and a first discharge port 605. The first eccentric portion 501 is sleeved with a first piston 606, and the first piston 606 is engaged with the first vane 603 to divide the inner space of the first cylinder 401 into a first suction chamber 607 communicated with the first suction port 604 and a first discharge chamber 608 communicated with the first discharge port 605.

Similarly, as shown in fig. 7, the second cylinder 402 has a second refrigerant flowing portion 701, a second vane 702, a second piston 703, a second suction port 704, a second discharge port 705, a second suction chamber 706, a second discharge chamber 707, and a second annular body 708. As shown in fig. 8, the third cylinder 403 includes a third refrigerant flow portion 801, a third vane 802, a third piston 803, a third suction port 804, a third discharge port 805, a third suction chamber 806, a third discharge chamber 807, and a third annular body 808. As shown in fig. 9, the fourth cylinder 404 has a fourth refrigerant circulating portion 901, a fourth vane 902, a fourth piston 903, a fourth suction port 904, a fourth discharge port 905, a fourth suction chamber 906, a fourth discharge chamber 907, and a fourth annular body 908.

As shown in fig. 4, the compressor further includes a first reservoir 409 and a second reservoir 410, a first suction port 604 and a second suction port 704 are connected to the first reservoir 409, and a third suction port 804 and a fourth suction port 904 are connected to the second reservoir 410.

The first suction chamber 607 and the fourth suction chamber 906 are point-symmetrical with respect to the center of the first cylinder 401, and the first discharge chamber 608 and the fourth discharge chamber 907 are point-symmetrical with respect to the center of the first cylinder 401. The second suction chamber 706 and the third suction chamber 806 are point-symmetrical with respect to the center of the first cylinder 401, and the second exhaust chamber 707 and the third exhaust chamber 807 are point-symmetrical with respect to the center of the first cylinder 401. The center of the first cylinder 401 and the center of the first annular body 602 coincide.

Referring to fig. 6 to 9, in a cross-section of the cylinder, an axis of the first suction port 604 and an axis of the first discharge port 605 are symmetrical with respect to a second predetermined line through which a corresponding first direction vector of the first refrigerant circulating part 601 passes. The axis of the second suction port 704 and the axis of the second discharge port 705 are symmetrical about a third predetermined line, and a second direction vector passing through the third predetermined line is correspondingly present in the second refrigerant flowing portion 701. The axes of the third suction port 804 and the third discharge port 805 are symmetrical about a fourth predetermined line, and a third direction vector passing through the fourth predetermined line is correspondingly present in the third refrigerant flowing portion 801. The axes of the fourth suction port 904 and the fourth discharge port 905 are symmetrical with respect to a fifth predetermined line, and a fourth directional vector passing through the fifth predetermined line is correspondingly present in the fourth refrigerant circulating part 901. The direction of the arrows in fig. 6 to 9 is the direction of the flow of the refrigerant gas inside the cylinder.

In this embodiment, the direction of the first direction vector is the same as that of the second direction vector. The third direction vector and the fourth direction vector have the same direction. The second direction vector and the third direction vector are opposite in direction. I.e. the angle between the second direction vector and the third direction vector is 180 deg..

The plane formed by the axis of the first suction port 604 and the axis of the third suction port 804 is perpendicular to the upper surface of the first cylinder 401. A plane formed by the axis of the second suction port 704 and the axis of the fourth suction port 904 is perpendicular to the upper surface of the first cylinder 401. The upper surface of the first cylinder 401 is a surface of the first cylinder 401 on the side closer to the upper cylinder head 406.

In another embodiment of the present application, the second predetermined line coincides with a center line of the first blade 603. The third predetermined line coincides with the center line of the second blade 702. The fourth predetermined line coincides with the center line of the third blade 802. The fifth predetermined line coincides with the center line of the fourth blade 902.

Referring to fig. 6 to 9, in the present embodiment, the phase difference between the first suction port 604 and the second suction port 704 is 0 °. The phase difference of the third suction port 804 and the fourth suction port 904 is 0 °. The first suction port 604 is 180 out of phase with the third suction port 804. The second suction port 704 has a phase difference of 180 ° from the fourth suction port 904. The angle between the first blade 603 and the second blade 702 is 0 °. The angle between third blade 802 and fourth blade 902 is 0 °. The angle between the second blade 702 and the third blade 802 is 180 °.

With continued reference to fig. 6-9, when the center point of the first piston 606 inside the first cylinder 401 rotates through an angle θ, then the center point of the second piston 703 inside the second cylinder 402 will rotate through an angle (θ +180 °). At the same time, the centre point of the third piston 803 inside the third cylinder 403 will rotate through an angle (θ +180 °), and the centre point of the fourth piston 903 inside the fourth cylinder 404 will rotate through an angle θ.

Since the first suction port 604 and the fourth suction port 904 have a phase difference of 180 °, and the first eccentric portion 501 and the fourth eccentric portion 504 are symmetrically disposed at 180 °, the volumes of the first suction chamber 607 and the fourth suction chamber 906 are equal, and the volumes of the first discharge chamber 608 and the fourth discharge chamber 907 are equal at any rotation angle of the crankshaft 408. Therefore, the forces of the gas in the first cylinder 401 and the gas in the fourth cylinder 404 on the crankshaft 408 are equal and opposite. Similarly, at any rotational angle of the crankshaft 408, the volumes of the second intake chamber 706 and the third intake chamber 806 are equal, and the volumes of the second exhaust chamber 707 and the third exhaust chamber 807 are equal. The forces on the crankshaft 408 from the gas in the second cylinder 402 and the gas in the third cylinder 403 are also equal and opposite. Referring to fig. 12, the force of all the cylinders acting on the crankshaft 408 is always constant to zero, which effectively reduces the gas force applied on the crankshaft 408, facilitates reducing the bending degree of the crankshaft 408, and facilitates improving the operation reliability of the compressor.

On the other hand, since the phase difference between the first suction port 604 and the second suction port 704 is 0 °, and the first eccentric portion 501 and the second eccentric portion 502 are symmetrically disposed at 180 °, so that the structure formed by the two cylinders is equivalent to a conventional double-cylinder compressor structure, and the resultant torque of the gas in the first cylinder 401 and the gas in the second cylinder 402 is the same as that of the double-cylinder compressor in the prior art. Similarly, the combined torque of the gas in the third cylinder 403 and the gas in the fourth cylinder 404 is also consistent with the prior art two-cylinder compressor. The resultant torque of the gas in the first cylinder 401 and the gas in the second cylinder 402 is equal to the resultant torque of the gas in the third cylinder 403 and the gas in the fourth cylinder 404, and has the same direction. Referring to fig. 11 and 13, on the premise that the number of cylinders is increased to achieve a large displacement, the moment fluctuation of the compressor provided by the present application is consistent with that of the conventional double-cylinder compressor in the prior art shown in fig. 1, and is relatively smooth, so that the compressor has low running noise.

Under the working condition of the compressor with the same displacement, the stress comparison schematic diagram of the crankshaft of the conventional single-cylinder rotary compressor and the conventional double-cylinder rotary compressor in the prior art is shown in figure 10, and the gas resultant moment comparison schematic diagram is shown in figure 11. The stress schematic diagram of the crankshaft is shown in fig. 12, and the gas resultant moment schematic diagram is shown in fig. 13. Referring to fig. 10 and 12, the resultant force experienced by the crankshaft of the present application is always zero, significantly less than that of the single and dual cylinder compressors of the prior art. The maximum value of the gas resultant torque and the fluctuation of the gas resultant torque are consistent with those of a double-cylinder compressor in the prior art, and are half of those of a single-cylinder compressor in the prior art. Therefore, even if the multi-cylinder rotary compressor designed according to the invention increases the discharge capacity of the compressor compared with the double-cylinder rotary compressor in the prior art shown in fig. 1, the resultant force borne by the crankshaft can still be ensured to be zero all the time, which is beneficial to ensuring the reliability of the compressor.

In another embodiment of the present application, the radial width of the second annular body 708 is equal to the radial width of the third annular body 808, the radial width of the first annular body 602 is equal to the radial width of the fourth annular body 908, and the radial width of the second annular body 708 is greater than the radial width of the first annular body 602, which is advantageous for improving the stability of the compressor during operation.

In another embodiment of the present application, the compressor has an accumulator to which the first suction port 604, the second suction port 704, the third suction port 804 and the fourth suction port 904 are connected.

In summary, the multi-cylinder rotary compressor of the present invention has at least the following advantages:

the multi-cylinder rotary compressor disclosed by the embodiment can effectively reduce the resultant force of gas borne by the crankshaft of the compressor, reduce the bending degree of the crankshaft, reduce the abrasion of the crankshaft and improve the operation reliability of the compressor on the premise of realizing large displacement and improving the refrigeration capacity of the compressor; moreover, the torque fluctuation is smooth, and the running noise is low.

In the description of the present invention, it is to be understood that the terms "bottom", "longitudinal", "lateral", "upper", "lower", "front", "rear", "vertical", "horizontal", and the like, indicate orientations and positional relationships based on the orientations and positional relationships shown in the drawings, are used only for convenience in describing the present invention and for simplification of description, and do not indicate or imply that the structures or elements referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus, are not to be construed as limiting the present invention. Furthermore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more and "several" means one or more unless otherwise specified.

In the description herein, references to the description of "one embodiment," "some embodiments," "an illustrative embodiment," "an example," "a specific example," etc., indicate that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

The foregoing is a more detailed description of the invention in connection with specific preferred embodiments and it is not intended that the invention be limited to these specific details. For those skilled in the art to which the invention pertains, several simple deductions or substitutions can be made without departing from the spirit of the invention, and all shall be considered as belonging to the protection scope of the invention.

Claims

1. A multi-cylinder rotary compressor, characterized in that, comprising a crankshaft and a plurality of cylinders;

The crankshaft is provided with a plurality of eccentric parts in the axial direction, the eccentric parts are arranged in a one-to-one correspondence with the cylinders, and the two adjacent eccentric parts are arranged at 180°±A°, where 0≤A° ≤45°;

The plurality of cylinders at least include a first cylinder, a second cylinder, a third cylinder and a fourth cylinder arranged in sequence along the axial direction of the crankshaft;

Each of the cylinders has a refrigerant circulation portion for sucking in and discharging refrigerant, the refrigerant circulation portion includes a suction port and an exhaust port, and in the cross section of each of the cylinders, the axis of the suction port is and the axis of the exhaust port to determine a preset line, the refrigerant circulation part has a direction vector passing through the preset line, the direction vector corresponding to the first cylinder and the direction vector corresponding to the second cylinder. The direction vector has the same direction, the direction vector corresponding to the third cylinder is in the same direction as the direction vector corresponding to the fourth cylinder, and the direction vector corresponding to the second cylinder is the same as the direction vector corresponding to the third cylinder. The corresponding direction vector forms an included angle ranging from 135° to 225°, and the cross section of the cylinder is a cross section perpendicular to the height direction thereof.

2 . The multi-cylinder rotary compressor according to claim 1 , wherein the compressor further comprises an upper cylinder head and a lower cylinder head, and the cylinders are arranged on the upper cylinder head and the lower cylinder head. 3 . Between the cylinder heads; the plane formed by the axis of the suction port of the first cylinder and the axis of the suction port of the third cylinder is perpendicular to the upper surface of the first cylinder, and the suction port of the second cylinder The plane formed by the axis of the port and the axis of the suction port of the fourth cylinder is perpendicular to the upper surface of the first cylinder, and the upper surface of the first cylinder is the first cylinder close to the upper cylinder head. side surface.

3 . The multi-cylinder rotary compressor according to claim 1 , wherein the suction port of the first cylinder and the suction port of the third cylinder have a phase difference of 180°, and the first cylinder has a phase difference of 180°. 4 . The intake port of the second cylinder and the intake port of the fourth cylinder have a phase difference of 180°, and the phase difference of the intake port of the first cylinder and the intake port of the second cylinder is 0°.

4 . The multi-cylinder rotary compressor according to claim 1 , wherein the cylinders are provided with vane grooves to accommodate vanes to slide, and the vanes corresponding to the first cylinder and the second cylinders The angle between the corresponding blades is 0°, the angle between the blade corresponding to the third cylinder and the blade corresponding to the fourth cylinder is 0°, the blade corresponding to the second cylinder and the blade corresponding to the fourth cylinder are 0°. The angle between the blades corresponding to the three cylinders is 180°.

5 . The multi-cylinder rotary compressor according to claim 4 , wherein a piston is sleeved on each of the eccentric parts, and the piston cooperates with the vanes to connect the inner space of the cylinder. 6 . It is divided into a suction chamber communicated with the suction port and an exhaust chamber communicated with the exhaust port; the suction chamber of the first cylinder and the suction chamber of the fourth cylinder are related to the first cylinder. The center of the cylinder is point-symmetrical, and the suction chamber of the second cylinder and the suction chamber of the third cylinder are point-symmetrical with respect to the center of the second cylinder.

6 . The multi-cylinder rotary compressor according to claim 5 , wherein the first cylinder and the fourth cylinder have the same suction chamber volume and the same exhaust chamber volume, and the second cylinder has the same volume. 7 . The volume of the suction cavity of the third cylinder is equal to that of the exhaust cavity.

7. The multi-cylinder rotary compressor according to claim 1, wherein the suction port is a circular hole, and the projection of the suction port on the cross section of the cylinder is relative to the suction port. The axis of the air port is symmetrical.

8 . The multi-cylinder rotary compressor according to claim 1 , wherein each of the cylinders has a hollow annular body, and the radial width of the annular body of the second cylinder is equal to that of the third cylinder. 9 . The radial width of the annular body of the first cylinder is equal to the radial width of the annular body of the fourth cylinder, and the radial width of the annular body of the second cylinder is greater than that of the first cylinder. The radial width of the annular body of a cylinder.

9 . The multi-cylinder rotary compressor according to claim 1 , wherein the plurality of cylinders are four cylinders, and the crankshaft is provided with four eccentric parts, which are respectively shafts along the crankshaft. 10 . The first eccentric part, the second eccentric part, the third eccentric part and the fourth eccentric part are arranged in sequence, the first eccentric part is located in the first cylinder, and the second eccentric part is located in the second cylinder wherein the third eccentric part is located in the third cylinder, and the fourth eccentric part is located in the fourth cylinder.

10. The multi-cylinder rotary compressor according to claim 1, wherein the compressor further comprises a first liquid accumulator and a second liquid accumulator, the suction port of the first cylinder and the second cylinder The suction ports of the third cylinder and the fourth cylinder are both connected to the second liquid reservoir.

11. The multi-cylinder rotary compressor according to claim 1, wherein the compressor further comprises a liquid accumulator, the suction port of the first cylinder, the suction port of the second cylinder, The suction port of the third cylinder and the suction port of the fourth cylinder are both connected to the accumulator.