CN210050033U - Rotary compressor and heat exchange equipment - Google Patents

Abstract

The utility model discloses a rotary compressor and heat exchange equipment, comprising: a casing; a driving mechanism, the driving mechanism is arranged in the casing; a compression mechanism, the compression mechanism is arranged in the casing and driven by the driving mechanism; a crankshaft, the crankshaft comprises The main shaft slidingly matched with the main bearing, the auxiliary shaft slidingly matching with the auxiliary bearing, and the eccentric shaft slidingly matching with the piston to drive the piston to rotate; A secondary shaft end hole is provided at the end, a shaft middle hole communicated with the secondary shaft end hole is arranged in the secondary shaft, and an exhaust hole connecting the shaft central hole and the inner space of the casing is arranged on the peripheral wall of the secondary shaft; the balance weight cover plate A closed cavity spaced from the inner space of the casing is defined between the balance weight cover plate and the compression mechanism, the countershaft balance weight and the auxiliary shaft end hole are located in the closed cavity, and the compression cavity communicates with the auxiliary shaft end hole through the closed cavity. According to the rotary compressor of the utility model, the lubricating oil and the counterweight of the countershaft do not interfere with each other, and the vibration and wear are small.

Description

Rotary compressors and heat exchange equipment

technical field

The utility model relates to the technical field of compressors, in particular to a rotary compressor and a heat exchange device having the rotary compressor.

Background technique

Compared with the two-cylinder rotary compressor, the single-cylinder rotary compressor mounted on the household air conditioner in the related art has advantages in energy efficiency, manufacturing cost, and productivity. However, since the balance weight that cancels the mass of the eccentric shaft and the piston of the single-cylinder rotary compressor is limited to the rotor of the motor, the motor torque fluctuation and the mass of the balance weight are large, resulting in large operating vibration, especially in the variable frequency type. During the high-speed operation of the motor, the bending of the crankshaft causes the wear of the sliding surfaces.

To this end, one method is to move the larger mass of the two balance weights fixed on the rotor of the motor to the lower end of the crankshaft, and use the balance weight cover plate to surround the balance weight that rotates with the crankshaft. The oil supply pump runs through the center of the counterweight cover, and the lubricating oil inside the casing flows into the counterweight cover, which will interfere with the high-speed rotation of the counterweight. Another method is to fix a counterweight with a large mass at the lower end of the crankshaft, and the counterweight rotates in the lubricating oil, which will disturb the lubricating oil. Another method is to increase the internal pressure of the counterweight cover to prevent the inflow of lubricating oil from the oil supply pump, but it will cause problems that interfere with the high-speed rotation of the counterweight.

Utility model content

The utility model aims to solve at least one of the technical problems existing in the prior art. To this end, the present utility model proposes a rotary compressor, which has the advantages of non-interference between lubricating oil and countershaft balance weight, small vibration, and low wear.

The utility model also proposes a heat exchange device with the rotary compressor.

The rotary compressor according to the embodiment of the first aspect of the present invention includes: a casing; a driving mechanism, the driving mechanism is provided in the casing; a compression mechanism, the compression mechanism is provided in the casing and is controlled by the The drive mechanism is driven, and the compression mechanism includes a cylinder, a first end plate and a second end plate that seal the opening surface of the cylinder, a main bearing arranged at the center of the first end plate, and a main bearing arranged at the center of the first end plate. A secondary bearing at the center of the second end plate, wherein the cylinder, the first end plate and the second end plate together define a compression chamber, and a compression chamber is provided in the cylinder along the inner peripheral wall of the cylinder. A rolling piston, the compression chamber is provided with a sliding vane that always stops on the outer peripheral surface of the piston and is suitable for reciprocating motion; a crankshaft, the crankshaft includes a main shaft slidingly matched with the main bearing, and the The auxiliary shaft is slidably matched with the auxiliary bearing, and the eccentric shaft is slidably matched with the piston to drive the piston to rotate; the auxiliary shaft balance weight is installed on the shaft end of the auxiliary shaft, and the auxiliary shaft The shaft end is provided with a secondary shaft end hole, the secondary shaft is provided with a shaft middle hole that communicates with the secondary shaft end hole, and the peripheral wall of the secondary shaft is provided with a connection between the shaft central hole and the housing. The exhaust hole of the inner space; the balance weight cover plate, a closed cavity spaced apart from the inner space of the casing is defined between the balance weight cover plate and the compression mechanism, the countershaft balance weight and the The auxiliary shaft end hole is located in the closed cavity, and the compression cavity communicates with the auxiliary shaft end hole through the closed cavity.

According to the rotary compressor of the embodiment of the present invention, the arrangement of the main counterweight is changed from the conventional motor rotor to the countershaft end of the crankshaft. Since the countershaft counterweight fixed to the countershaft end is sealed by the counterweight cover plate, it is possible to The inflow of lubricating oil is prevented, and by changing the traditional splash lubrication method to a spray lubrication method, it is possible to seal the countershaft counterweight through the counterweight cover plate.

In addition, the rotary compressor according to the embodiment of the present invention also has the following additional technical features:

According to some embodiments of the present invention, a discharge hole is provided on the second end plate, and the discharge hole communicates with the compression cavity and the airtight cavity.

According to some embodiments of the present invention, the counterweight cover plate is covered on the outer peripheral wall of the second end plate.

According to some embodiments of the present invention, any one of the first end plate and the second end plate is provided with an oil injection hole, and an oil injection pipe is provided in the housing, and the oil injection pipe passes through the oil injection hole Fill the compression chamber with oil.

According to some embodiments of the present invention, the lower end of the auxiliary shaft extends downward to form an extension shaft, the auxiliary shaft balance weight is sleeved on the extension shaft, and the auxiliary shaft end hole is formed on the extension shaft end of the shaft.

According to some embodiments of the present invention, the main shaft, the secondary shaft and the eccentric shaft are respectively provided with air injection holes and oil grooves, the oil grooves extend along the axial direction of the crankshaft, the air injection holes and the oil grooves connected.

Further, the air injection hole and the oil groove are located between the secondary shaft end hole and the exhaust hole.

According to some embodiments of the present invention, the axis of rotation of the counterweight of the countershaft coincides with the axis of rotation of the eccentric shaft and the axis of rotation of the piston, and the counterweight of the countershaft rotates to generate a The centrifugal force generated is the opposite direction of the centrifugal force.

According to some embodiments of the present invention, the driving mechanism includes: a stator mounted on the inner peripheral wall of the housing; a rotor for driving the crankshaft to rotate, the rotor is arranged in the stator, the rotor is There is a rotor balance weight on it; the motor coil is arranged on the stator.

Further, the sum of the centrifugal force of the countershaft balance weight and the rotor balance weight is equal to the sum of the centrifugal force of the eccentric shaft and the piston.

The heat exchange device according to the embodiment of the second aspect of the present invention includes the rotary compressor according to the embodiment of the first aspect of the present invention.

According to the heat exchange equipment of the embodiment of the present invention, using the rotary compressor as described above, the lubricating oil and the counterweight of the countershaft do not interfere with each other, and the vibration and wear are small.

Additional aspects and advantages of the invention will be set forth, in part, from the following description, and in part will be apparent from the following description, or learned by practice of the invention.

Description of drawings

1 is a cross-sectional view of a rotary compressor according to an embodiment of the present invention;

2 is a partial cross-sectional view of a rotary compressor according to an embodiment of the present invention;

3 is a schematic structural diagram of a countershaft counterweight of a rotary compressor according to an embodiment of the present invention;

4 is a cross-sectional view of a counterweight of a countershaft of a rotary compressor according to an embodiment of the present invention.

Reference number:

Rotary compressor 1, casing 2, exhaust pipe 3, suction pipe 4, compression mechanism 5, motor 6, stator 7, motor coil 7a, rotor 8, rotor rivet 8a, lubricating oil 9, first end plate 10 , main bearing 10a, cylinder 15, compression chamber 15a, piston 16, sliding vane 18, second end plate 20, auxiliary bearing 20a, oil injection pipe 22, oil injection hole 23, screw 24, crankshaft 25, main shaft 26, auxiliary shaft 27, Extension shaft 27a, auxiliary shaft end hole 27b, eccentric shaft 28, shaft center hole 29, air injection holes 26a, 28a, 29a, auxiliary shaft balance weight 30, balance main part 30a, fixing hole 30c, rivet hole 30d, through rivet 31, Rotor balance weight 32 , balance weight cover plate 35 , exhaust hole 40 , discharge hole 45 , condenser 50 , expansion valve 51 , evaporator 52 , and accumulator 53 .

Detailed ways

The following describes in detail the embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein the same or similar reference numerals refer to the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, but should not be construed as a limitation of the present invention.

The rotary compressor 1 according to the embodiment of the first aspect of the present invention will be described below with reference to the accompanying drawings.

As shown in Fig. 1 , a rotary compressor 1 includes an inverter-type motor 6 (that is, a drive mechanism) and a compression mechanism 5 fixed to the inner periphery of a hermetically sealed high-pressure casing 2, and a lubricating oil 9 is sealed at the bottom of the casing 2. In the compression mechanism 5 , the main shaft 26 and the auxiliary shaft 27 of the crankshaft 25 are respectively connected with the cylinder 15 fixed to the inner circumference of the casing 2 , the first end plate 10 and the second end plate 20 fixed on the upper and lower sides of the cylinder 15 , and The main bearing 10a and the auxiliary bearing 20a, respectively provided in the center of these end plates, are slidably fitted. The eccentric shaft 28 on the crankshaft 25 eccentrically rotates the piston 16 arranged in the compression chamber 15 a , and the vane 18 in contact with the outer periphery of the piston 16 reciprocates along the vane groove of the cylinder 15 .

The inverter-type motor 6 is composed of a stator 7 fixed on the inner circumference of the casing 2, a rotor 8 that drives the crankshaft 25 to rotate at its inner diameter, and a motor coil 7a arranged on the stator 7. A counterweight 30 is fixed to the lower portion of the countershaft 27 of the crankshaft 15 by through rivets 31 .

As shown in FIG. 2 , the rotation centerline of the counterweight 30 of the countershaft is consistent with the rotation centerline of the eccentric shaft 28 of the crankshaft 25 and the piston 16 , and the centrifugal force generated by the rotation of the counterweight 30 is opposite to the centrifugal force generated by the rotation of the crankshaft 25 . For example, the balance main portion 30 a of the countershaft counterweight 30 is radially opposed to the eccentric main portion of the eccentric shaft 28 . Since the countershaft counterweight 30 is sealed by the counterweight cover plate 35 fixed to the outer circumference of the second end plate 20, the countershaft counterweight 30 does not interfere with the lubricating oil 9 accumulated at the bottom of the casing 2, and can be easily installed on the counterweight The cover plate 35 is rotated from a low speed to a high speed.

The counterweight cover plate 35 is fixed to the outer periphery of the second end plate 20 with screws, or fixed by a fixing method such as spot welding or laser welding at multiple locations. Alternatively, the counterweight cover plate 35 can also be fixed by a plurality of screws 24 connecting the second end plate 20 and the cylinder 15, but since the inner volume of the counterweight cover plate 35 is reduced, there is a degree of freedom in the design of the countershaft counterweight 30 Damaged disadvantages. In addition, since the internal pressure of the counterweight cover 35 during operation is higher than the internal pressure of the casing 2, if the clearance of the fixed portion of the counterweight cover 35 is small, the lubricating oil 9 does not flow in.

As shown in FIG. 1 , before the countershaft counterweight 30 is installed, a relatively light rotor counterweight 32 is fixed on the upper end of the rotor 8 . The rotor balance weight 32 is fixed to the upper end of the rotor 8 by two of the four rotor rivets 8 a used for assembling the rotor 8 . In addition, the rotor counterweight 32 may be arranged at the lower end of the rotor 8, but since the moment decreases, the mass of the counterweight needs to be increased.

In order to minimize the vibration in the normal direction of the rotary compressor 1, during the compressor operation, the sum of the centrifugal force of the countershaft counterweight 30 and the rotor counterweight 32 is equal to the sum of the centrifugal force of the opposite eccentric shaft 28 and the piston 16, With reference to the center of rotation of the sum of the masses of the eccentric shaft 28 and the piston 16 , the torque of the countershaft counterweight 30 and the rotor counterweight 32 must be equal.

As a result, Fa=Fo·Lb/(Lb+La) and Fb=Fo·La/(Lb+La) are satisfied. Fo, Fa, and Fb are the sum of the centrifugal force of the eccentric shaft 28 and the piston 16 , the centrifugal force of the countershaft counterweight 30 , and the centrifugal force of the rotor counterweight 32 , respectively. La and Lb are respectively the dimension from the centrifugal force center of the piston 16 to the centrifugal force center of the countershaft counterweight 30 and the dimension from the centrifugal force center of the piston 16 to the centrifugal force center of the rotor counterweight 32 . If the dimensions of Fo, La and Lb are predetermined, the design of the countershaft counterweight 30 and the rotor counterweight 32 can be simplified.

As shown in FIG. 3 and FIG. 4 , the counterweight 30 can be formed by sintering powder alloy or by forging from steel. Since the fixing hole 30c is a hole for inserting the auxiliary shaft 27 for fixing, it is necessary to reduce the gap with the outer diameter of the auxiliary shaft 27 as much as possible. In addition, the method of heating the counterweight 30 to shrink-fit is also effective.

The rivet hole 30d is a hole through which the through rivet 31 passes. The counterweight 30 of the counter shaft is inserted into the extension shaft 27a and then inserted into the through rivet 31. One rivet end needs to be punched. In addition, the penetration rivet 31 does not affect the resistance of the oil-containing refrigerant gas passing through the shaft hole 29, and the inner diameter of the extension shaft 27a can be enlarged if necessary.

Due to the introduction of a new spray lubrication method in the rotary compressor 1 , the high-pressure spray lubrication gas passes through the counter balance weight 30 and the inside of the crankshaft 29 . The lubrication method and the refrigerant and lubricating oil circulating in the refrigeration cycle device will be described below with reference to FIG. 1 . Wherein, the refrigeration cycle device may be an air conditioner.

The low-pressure refrigerant flowing into the compression chamber 15a from the suction pipe through the refrigeration cycle device, that is, the refrigerant circulating in the refrigeration cycle device contains circulating oil in a weight ratio of about 1%. In addition, since the internal pressure of the casing 2 is high pressure, when the amount of lubricating oil flowing out from the inner diameter of the piston 16 and the sliding gap of the vane 18 to the compression chamber 15a is about 2%, the refrigerant gas compressed in the compression chamber 15a contains about 2%. 3% lube oil.

The lubricating oil becomes spray oil due to the compression temperature of the compression chamber 15a, and the high pressure refrigerant gas discharged to the counterweight cover plate 35 through the discharge hole 45 on the second end plate 20 contains about 3% of the spray lubricating oil. After that, the high-pressure refrigerant gas flows into the shaft center hole 29 of the crankshaft 25 from the counter shaft end hole 27 b after being stirred by the rotation of the counter shaft counterweight 30 .

At this time, as shown in FIG. 2 , the secondary shaft 27 , the eccentric shaft 28 and the main shaft 26 respectively have injection holes 26a, 28a, 29a and oil grooves for detouring the high-pressure refrigerant gas, and spray lubricating oil to lubricate the outer peripheral sliding surface of the crankshaft 25. The remaining spray lubricating oil is discharged to the inside of the casing 2 from the exhaust hole 40 of the main shaft 26 together with the refrigerant gas.

After that, as shown in FIG. 1 , the high-pressure gas with the oil content reduced to about 1% passes through the gap between the outer peripheral gap 7 b of the stator 7 and the high-temperature motor coil 7 a , and is discharged from the exhaust pipe 3 , and passes through the condenser 50 and the expansion valve 51 . , the evaporator 52, the accumulator 53, and the suction pipe 4 flow into the compression chamber 15a again. Through this refrigeration cycle, continuous spray lubrication in the compression mechanism 5 is established. In addition, the counterweight cover plate 35 is not only a rotating chamber of the counter-shaft counterweight 30, but also an exhaust muffler for the high-pressure refrigerant discharged from the compression chamber 15a.

That is, the oil-containing refrigerant gas discharged from the compression chamber 15a provided in the center of the cylinder 15 to the counterweight cover plate 35 passes from the countershaft end hole 27b through the shaft hole 29, lubricates the sliding parts of the crankshaft 25 and the piston 16, The vent hole 40 of the main shaft 26 discharges. The counterweight 30 fixed to the extension shaft 27 a of the countershaft 27 of the crankshaft 25 is sealed by the counterweight cover plate 35 . In addition to preventing the inflow of the lubricating oil 9, the counterweight cover plate 35 also serves as a silencer for the gas discharged from the compression chamber 15a.

Among them, the designed sliding clearance of the crankshaft 25 and the like is about 20 μm, and the thickness of the oil film during operation is 1 μm (maximum load portion) to 20 μm (minimum load portion). Therefore, the amount of lubricating oil required for the outer diameter sliding surface or the sliding surface of the piston 16 is small, and an amount of lubricating oil of about 3% by weight of the refrigerant is sufficient to lubricate the sliding surfaces. In addition, the sliding surface of the sliding vane 18 is lubricated by the pressure difference with the compression chamber 15a, and oil is supplied from the lubricating oil 9 in the casing 2. That is, the lubrication method of the vanes 18 is the same as that of the conventional rotary compressor.

The oil injection pipe 22 shown in FIGS. 1 and 2 is a means (fuel injection method) for increasing the concentration of the sprayed lubricating oil by injecting the lubricating oil 9 at the bottom of the casing 2 into the compression chamber 15a when the above-mentioned 3% oil amount is insufficient. In addition, the oil filling pipe 22 and the oil filling hole 23 may be provided in the first end plate 10. However, the above-mentioned oil supply means may be omitted if not required.

As described above, according to the rotary compressor 1 of the embodiment of the present invention, by introducing the spray lubrication method, a sealed counterweight cover plate 35 can be used. It can be said that the countershaft counterweight 30 is fixed on the countershaft 27 to make it operate as possible. In addition, by enlarging the design freedom of the counterweight cover 35, the counterweight 30 having a heavy weight can be used, so that an inverter capable of high-speed operation can be introduced and the single-cylinder rotary compressor can be increased in size.

According to the rotary compressor 1 of the embodiment of the present invention, the wear problem of the inner diameter of the main bearing of the single-cylinder rotary compressor can be completely solved, and the vibration problem of the compressor caused by the design limitation of the counterweight can be solved.

In addition, the rotary compressor 1 according to the embodiment of the present invention may be a multi-cylinder rotary compressor, a swing rotary compressor in which a piston and a sliding vane are integrated, a horizontal rotary compressor, or the like. The utility model needs to change part of the design of the conventional rotary compressor, but the conventional manufacturing equipment can be used.

Other structures and operations of the rotary compressor 1 according to the embodiment of the present invention are known to those of ordinary skill in the art, and will not be described in detail here.

The heat exchange device according to the embodiment of the second aspect of the present invention includes the rotary compressor 1 according to the embodiment of the first aspect of the present invention. For example, the heat exchange equipment may be air conditioners, refrigeration equipment, and heat pump water heaters.

According to the heat exchange equipment of the embodiment of the present invention, using the rotary compressor 1 as described above, the lubricating oil and the counterweight of the countershaft do not interfere with each other, and the vibration and wear are small.

In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "Back", "Left", "Right", "Vertical", "Horizontal", "Top", "Bottom", "Inner", "Outer", "Clockwise", "Counterclockwise", "Axial" ", "radial", "circumferential" and other indicated orientations or positional relationships are based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying the indicated A device or element must have a specific orientation, be constructed and operate in a specific orientation, and therefore should not be construed as a limitation of the present invention.

In addition, the terms "first" and "second" are only used for descriptive purposes, and should not be construed as indicating or implying relative importance or implying the number of indicated technical features. Thus, a feature defined as "first" or "second" may expressly or implicitly include one or more of that feature. In the description of the present invention, unless otherwise specified, "plurality" means two or more.

In the description of the present invention, "first feature" and "second feature" may include one or more of the features, and the first feature "above" or "under" the second feature may include the first and The second feature is in direct contact, and may also include that the first and second features are not in direct contact but are in contact through another feature therebetween. The first feature is "above", "over" and "above" the second feature includes the first feature being directly above and diagonally above the second feature, or simply means that the first feature is level higher than the second feature.

It should be noted that, in the description of the present invention, unless otherwise expressly specified and limited, the terms "installed", "connected" and "connected" should be understood in a broad sense, for example, it may be a fixed connection or a connectable connection. Detachable connection, or integral connection; may be mechanical connection or electrical connection; may be direct connection, indirect connection through an intermediate medium, or internal communication between two components. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood in specific situations.

In the description of this specification, references to the terms "one embodiment," "some embodiments," "specific embodiments," "examples," or "some examples", etc., mean specific features described in connection with the embodiment or example. , structure, material or feature is included in at least one embodiment or example of the present invention. In this specification, schematic representations of the above terms 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.

Although embodiments of the present invention have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and alterations can be made in these embodiments without departing from the principles and spirit of the invention. Variations, the scope of the present invention is defined by the claims and their equivalents.

Claims (11)

1. A rotary compressor, comprising:

a housing;

the driving mechanism is arranged in the shell;

the compression mechanism is arranged in the shell and driven by the driving mechanism, and comprises a cylinder, a first end plate and a second end plate which seal an opening surface of the cylinder, a main bearing arranged at the center of the first end plate, and an auxiliary bearing arranged at the center of the second end plate, wherein the cylinder, the first end plate and the second end plate jointly define a compression cavity, a piston which can roll along the inner peripheral wall of the cylinder is arranged in the cylinder, and a sliding vane which normally abuts against the outer peripheral surface of the piston and is suitable for reciprocating motion is arranged in the compression cavity;

the crankshaft comprises a main shaft in sliding fit with the main bearing, a secondary shaft in sliding fit with the secondary bearing, and an eccentric shaft in sliding fit with the piston to drive the piston to rotate;

the auxiliary shaft counterweight is arranged at the shaft end of the auxiliary shaft, an auxiliary shaft end hole is formed in the shaft end of the auxiliary shaft, a shaft middle hole communicated with the auxiliary shaft end hole is formed in the auxiliary shaft, and an exhaust hole communicated with the shaft middle hole and the inner space of the shell is formed in the peripheral wall of the auxiliary shaft;

the balance weight cover plate is arranged on the balance weight cover plate, a closed cavity which is spaced from the inner space of the shell is defined between the balance weight cover plate and the compression mechanism, the auxiliary shaft balance weight and the auxiliary shaft end hole are arranged in the closed cavity, and the compression cavity is communicated with the auxiliary shaft end hole through the closed cavity.

2. The rotary compressor of claim 1, wherein the second end plate is provided with a discharge hole, and the discharge hole communicates the compression chamber and the hermetic chamber.

3. The rotary compressor of claim 1, wherein the counterweight cover plate is disposed at the outer peripheral wall of the second end plate.

4. The rotary compressor of claim 1, wherein an oil injection hole is provided on either one of the first end plate and the second end plate, and an oil injection pipe is provided in the casing, and the oil injection pipe injects oil into the compression chamber through the oil injection hole.

5. The rotary compressor of claim 1, wherein a lower end of the auxiliary shaft extends downward to form an extension shaft, the auxiliary shaft balance weight is fitted over the extension shaft, and the auxiliary shaft end hole is formed at an end of the extension shaft.

6. The rotary compressor of claim 1, wherein the main shaft, the auxiliary shaft, and the eccentric shaft are provided with a gas injection hole and an oil groove, respectively, the oil groove extending in an axial direction of the crankshaft, the gas injection hole being connected to the oil groove.

7. The rotary compressor of claim 6, wherein the gas injection holes and the oil sump are located between the secondary shaft end holes and the discharge hole.

8. The rotary compressor of claim 1, wherein a rotational axis of the counter weight coincides with a rotational axis of the eccentric shaft and a rotational axis of the piston, the counter weight rotating to generate a centrifugal force in a direction opposite to a centrifugal force generated by rotation of the crankshaft.

9. The rotary compressor of claim 1, wherein the driving mechanism comprises:

a stator mounted on an inner circumferential wall of the housing;

the rotor is used for driving the crankshaft to rotate, the rotor is arranged in the stator, and a rotor counterweight is arranged on the rotor;

a motor coil disposed on the stator.

10. The rotary compressor of claim 9, wherein a sum of centrifugal forces of the counter-shaft balancing weight and the rotor balancing weight is equal to a sum of centrifugal forces of the eccentric shaft and the piston.

11. A heat exchange apparatus comprising a rotary compressor according to any one of claims 1 to 10.

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