CN210050033U - Rotary compressor and heat exchange equipment - Google Patents

Abstract

The utility model discloses a rotary compressor and indirect heating equipment, include: a housing; the driving mechanism is arranged in the shell; the compression mechanism is arranged in the shell and is driven by the driving mechanism; the crankshaft comprises a main shaft in sliding fit with the main bearing, an auxiliary shaft in sliding fit with the auxiliary 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; balanced heavy apron, the airtight chamber spaced apart with the inner space of casing is injectd between balanced heavy apron and the compression mechanism, and balanced heavy and countershaft end hole of countershaft is arranged in airtight chamber, and the compression chamber passes through airtight chamber and countershaft end hole intercommunication. According to the utility model discloses a rotary compressor, lubricating oil and counter shaft counter weight noninterference, vibration are little, wearing and tearing are little.

Description

Rotary compressor and heat exchange equipment

Technical Field

The utility model relates to a compressor technical field particularly, relates to a rotary compressor and have rotary compressor's indirect heating equipment.

Background

The single-cylinder rotary compressor mounted on the home air conditioner in the related art has advantages in energy efficiency, manufacturing cost, and productivity, compared to the double-cylinder rotary compressor. However, since the balance weight, which is offset from the sum of the masses of the eccentric shaft and the piston of the single cylinder rotary compressor, is defined on the rotor of the motor, the motor moment fluctuation and the balance weight mass are large, resulting in large operation vibration, and particularly, in high-speed operation of the inverter type motor, the crankshaft is bent to cause abrasion of the sliding surface.

Therefore, one method is to move the heavy weight with a large mass out of two weights fixed on the motor rotor to the lower end of the crankshaft, and surround the weight rotating together with the crankshaft with a weight cover plate. Another method is to fix a counterweight with a large mass at the lower end of the crankshaft, which rotates in the lubricating oil, and which can disturb the lubricating oil. There is also a method of increasing the internal pressure of the counterweight cover plate to prevent the lubricating oil from flowing from the oil supply pump, but there is a problem that the high-speed rotation of the counterweight is disturbed.

SUMMERY OF THE UTILITY MODEL

The utility model discloses aim at solving one of the technical problem that exists among the prior art at least. Therefore, the utility model provides a rotary compressor, rotary compressor has lubricating oil and the counter shaft balanced weight noninterfere, the vibration is little, wearing and tearing advantage such as little.

The utility model discloses still provide one kind and have rotary compressor's indirect heating equipment.

According to the utility model discloses rotary compressor of first aspect embodiment includes: 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.

According to the utility model discloses rotary compressor changes the vice axle head of bent axle with the configuration of main balanced heavy from electric motor rotor in the past, owing to fix the counter balance heavy by balanced heavy apron at vice axle head and seal to can prevent that lubricating oil from flowing into, and, through changing traditional splash lubrication method into spray lubrication method, can realize sealing the counter balance heavy through balanced heavy apron.

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

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

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

According to the utility model discloses a some embodiments, first end plate with be equipped with the oil filler point on any in the second end plate, be equipped with the oiling pipe in the casing, the oiling pipe passes through the oil filler point to compression chamber oiling.

According to some embodiments of the present invention, the lower end of the countershaft extends downward to form an extension shaft, the countershaft counterweight sleeve is disposed on the extension shaft, and the countershaft end hole is formed at the shaft end of the extension shaft.

According to some embodiments of the utility model, the main shaft the countershaft with the eccentric shaft is equipped with fumarole and oil groove respectively, the oil groove is followed the axial extension of bent axle, the fumarole with the oil groove links to each other.

Further, the gas injection holes and the oil groove are located between the secondary shaft end holes and the exhaust holes.

According to some embodiments of the invention, the axis of rotation of the counter weight coincides with the axis of rotation of the eccentric shaft and the axis of rotation of the piston, the counter weight when rotating generating a centrifugal force in the opposite direction to the centrifugal force generated by the rotation of the crankshaft.

According to some embodiments of the invention, the drive 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.

Further, a sum of centrifugal forces of the counter weight and the rotor weight is equal to a sum of centrifugal forces of the eccentric shaft and the piston.

According to the utility model discloses indirect heating equipment of second aspect embodiment, include according to the utility model discloses the first aspect embodiment rotary compressor.

According to the utility model discloses indirect heating equipment utilizes as above rotary compressor, lubricating oil and the balanced mutually noninterfere of countershaft, the vibration is little, wearing and tearing are little.

Additional aspects and advantages of the invention will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the invention.

Drawings

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

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

fig. 3 is a schematic structural view of a counter balance of a counter shaft of a rotary compressor according to an embodiment of the present invention;

fig. 4 is a sectional view of a counter balance of a rotary compressor according to an embodiment of the present invention.

Reference numerals:

the rotary compressor comprises a rotary compressor 1, a shell 2, an exhaust pipe 3, an air suction pipe 4, a compression mechanism 5, a motor 6, a stator 7, a motor coil 7a, a rotor 8, a rotor rivet 8a, lubricating oil 9, a first end plate 10, a main bearing 10a, a cylinder 15, a compression cavity 15a, a piston 16, a slide vane 18, a second end plate 20, a secondary bearing 20a, an oil filling pipe 22, an oil filling hole 23, a screw 24, a crankshaft 25, a main shaft 26, a secondary shaft 27, an extension shaft 27a, a secondary shaft end hole 27b, an eccentric shaft 28, a shaft center hole 29, air injection holes 26a, 28a and 29a, a secondary shaft balance weight 30, a balance main part 30a, a fixing hole 30c, a rivet hole 30d, a through rivet 31, a rotor balance weight 32, a balance weight cover plate 35, an exhaust hole 40, an exhaust hole 45, a.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are exemplary only for the purpose of explaining the present invention, and should not be construed as limiting the present invention.

A rotary compressor 1 according to an embodiment of a first aspect of the present invention is described below with reference to the accompanying drawings.

As shown in fig. 1, the rotary compressor 1 includes an inverter-type motor 6 (i.e., a drive mechanism) and a compression mechanism 5 fixed to the inner periphery of a sealed high-pressure casing 2, and a lubricant 9 is sealed in the bottom of the casing 2. In the compression mechanism 5, the main shaft 26 and the sub shaft 27 of the crankshaft 25 are slidably engaged with the cylinder 15 fixed to the inner periphery of the casing 2, the first end plate 10 and the second end plate 20 fixed to the upper and lower surfaces of the cylinder 15, and the main bearing 10a and the sub bearing 20a provided at the centers of these end plates, respectively. The eccentric shaft 28 on the crankshaft 25 eccentrically rotates the piston 16 disposed in the compression chamber 15a, and the vane 18 abutting 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 to the inner periphery of the housing 2, a rotor 8 rotating a crankshaft 25 at its inner diameter, and a motor coil 7a disposed on the stator 7. A counter weight 30 is fixed to a lower portion of the counter shaft 27 of the crankshaft 15 by a through rivet 31.

As shown in fig. 2, the rotation center line of the counter balance weight 30 coincides with the rotation center line of the eccentric shaft 28 of the crankshaft 25 and the piston 16, the centrifugal force generated by the rotation of the counter balance weight 30 is opposite to the centrifugal force generated by the rotation of the crankshaft 25, and the main balance portion 30a of the counter balance weight 30 is radially opposed to the eccentric main portion of the eccentric shaft 28. Since the counter balance weight 30 is sealed by the balance weight cover plate 35 fixed to the outer periphery of the second end plate 20, the counter balance weight 30 does not interfere with the lubricating oil 9 accumulated at the bottom of the housing 2, and it is possible to easily change from low-speed rotation to high-speed rotation in the balance weight cover plate 35.

The counterweight cover plate 35 is fixed to the outer periphery of the second end plate 20 by screws or by fixing methods such as spot welding or laser welding. Further alternatively, the counterweight cover 35 may be fixed by a plurality of screws 24 connecting the second end plate 20 and the cylinder 15, but since the internal volume of the counterweight cover 35 is reduced, there is a disadvantage that the degree of freedom in designing the counter weight 30 is impaired. In addition, since the internal pressure of the counterweight cover plate 35 in operation is higher than the internal pressure of the housing 2, if the clearance of the fixed portion of the counterweight cover plate 35 is small, the lubricating oil 9 does not flow in.

As shown in fig. 1, before the counter balance weight 30 is mounted, a rotor balance weight 32 having a light weight is fixed to the upper end of the rotor 8. The rotor balance weight 32 is fixed to the upper end of the rotor 8 by 2 of 4 rotor rivets 8a used for assembling the rotor 8. The rotor balance weight 32 may be disposed at the lower end of the rotor 8, but since the moment is reduced, the weight of the balance weight needs to be increased.

In order to minimize the vibration in the normal direction of the rotary compressor 1, the sum of the centrifugal forces of the counter balance weight 30 and the rotor balance weight 32 is equal to the sum of the centrifugal forces of the eccentric shaft 28 and the piston 16 facing each other during the operation of the compressor, and the counter balance weight 30 and the rotor balance weight 32 must have the same torque with respect to the rotation center of the sum of the masses of the eccentric shaft 28 and the piston 16.

As a result, Fa is Fo · Lb/(Lb + La), and Fb is Fo · La/(Lb + La) are satisfied. Fo, Fa, Fb are the sum of the centrifugal forces of the eccentric shaft 28 and the piston 16, the centrifugal force of the counter balance 30, and the centrifugal force of the rotor balance 32, respectively. La and Lb are the size from the centrifugal force center of the piston 16 to the centrifugal force center of the counter weight 30 and the size from the centrifugal force center of the piston 16 to the centrifugal force center of the rotor weight 32, respectively. The design of the counter weight 30 and the rotor weight 32 is simplified if Fo, La and Lb are dimensioned in advance.

As shown in fig. 3 and 4, the counter balance weight 30 may be formed by sintering a powder alloy or by forging a steel material. Since the fixing hole 30c is a hole into which the auxiliary shaft 27 is inserted for fixing, it is necessary to reduce the clearance with the outer diameter of the auxiliary shaft 27 as much as possible. In addition, a method of heating the counter balance weight 30 to shrink the jacket is also effective.

The rivet hole 30d is a hole through which the through rivet 31 passes, and the counter weight 30 is inserted into the extension shaft 27a and then into the through rivet 31, and one rivet end needs to be press-formed. The through rivet 31 does not affect the resistance of the refrigerant gas containing oil passing through the shaft center hole 29, and the inner diameter of the extension shaft 27a may be enlarged if necessary.

Since the rotary compressor 1 adopts a new spray lubrication method, the high-pressure spray lubrication gas passes through the counter balance 30 and the crankshaft 29. The lubrication method and the refrigerant and the lubricating oil circulating in the refrigeration cycle apparatus will be described below with reference to fig. 1. Wherein, the refrigeration cycle device can be an air conditioner.

The low-pressure refrigerant flowing from the suction pipe into the compression chamber 15a through the refrigeration cycle apparatus, i.e., the refrigerant circulating through the refrigeration cycle apparatus, contains about 1% by weight of circulating oil. Further, since the internal pressure of the casing 2 is high, when the amount of the lubricating oil flowing out of the inner diameter of the piston 16 and the sliding gap between the vanes 18 to the compression chamber 15a is about 2%, the refrigerant gas compressed in the compression chamber 15a contains about 3% of the lubricating oil.

The lubricant oil becomes a spray oil by the temperature rise of the compression in the compression chamber 15a, and the high-pressure refrigerant gas discharged to the counterweight cover plate 35 through the discharge holes 45 in the second end plate 20 contains about 3% of the spray lubricant oil. Thereafter, the high-pressure refrigerant gas is stirred by the rotation of the counter weight 30, and then flows into the shaft center hole 29 of the crankshaft 25 from the counter end hole 27 b.

At this time, as shown in fig. 2, the auxiliary shaft 27, the eccentric shaft 28, and the main shaft 26 have gas injection holes 26a, 28a, and 29a through which high-pressure refrigerant gas flows, and oil grooves, respectively, and the lubricant oil is sprayed to lubricate the outer peripheral sliding surface of the crankshaft 25. The surplus sprayed lubricating oil is discharged from the discharge hole 40 of the main shaft 26 into the interior of the housing 2 together with the refrigerant gas.

Thereafter, as shown in fig. 1, the high-pressure gas having an oil content reduced to about 1% is discharged from the exhaust pipe 3 through the gap between the outer circumferential gap 7b of the stator 7 and the high-temperature motor coil 7a, and flows into the compression chamber 15a again through the condenser 50, the expansion valve 51, the evaporator 52, the accumulator 53, and the intake pipe 4. By this refrigeration cycle, continuous spray lubrication in the compression mechanism 5 is established. The counterweight cover plate 35 serves not only as a rotation chamber of the counter weight 30 but also as an exhaust muffler for high-pressure refrigerant discharged from the compression chamber 15 a.

That is, the oil-containing refrigerant gas discharged from the compression chamber 15a provided at the center of the cylinder 15 to the counter weight cover 35 is discharged from the discharge port 40 of the main shaft 26 after lubricating the sliding portions of the crankshaft 25 and the piston 16 from the auxiliary shaft end hole 27b via the shaft center hole 29. The counter weight 30 fixed to the extension shaft 27a of the counter shaft 27 of the crankshaft 25 is sealed by a counter weight cover 35. The counterweight cover plate 35 serves as a muffler for the gas discharged from the compression chamber 15a, in addition to preventing the lubricant oil 9 from flowing in.

The design 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 lubricant required for the outer diameter sliding surface or the sliding surface of the piston 16 is small, and the amount of lubricant is sufficient to lubricate the sliding surface by about 3% by weight of the refrigerant. The sliding surface of the vane 18 is lubricated by the pressure difference with the compression chamber 15a, and is supplied with oil from the lubricating oil 9 in the casing 2. That is, the vane 18 is lubricated in the same manner as in the conventional rotary compressor.

In the filler pipe 22 shown in fig. 1 and 2, when the amount of oil of 3% is insufficient, the lubricant oil 9 at the bottom of the casing 2 is injected into the compression chamber 15a to increase the concentration of the sprayed lubricant oil (oil spray method). Further, the filler pipe 22 and the filler hole 23 may be provided in the first end plate 10. However, the above 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, the sealed counterweight cover plate 35 can be adopted by introducing the spray lubrication method, and it can be said that the auxiliary shaft counterweight 30 is fixed to the auxiliary shaft 27 to enable the operation thereof. Further, since the counter balance weight 30 having a large weight can be used by increasing the degree of freedom in designing the balance weight cover 35, it is possible to introduce an inverter capable of operating at a high speed and to increase the size of the single cylinder rotary compressor.

According to the utility model discloses rotary compressor 1 can thoroughly solve the internal diameter wearing and tearing problem of single cylinder rotary compressor's main bearing, can solve the vibration problem of the compressor that leads to because of balanced heavy design restriction.

Furthermore, according to the utility model discloses rotary compressor 1 can be multi-cylinder rotary compressor, the swing rotary compressor of piston and gleitbretter integration, horizontal rotary compressor etc.. The utility model discloses need to change the partial design of rotary compressor in the past, nevertheless can continue to use former manufacture equipment.

Other constructions and operations of the rotary compressor 1 according to the embodiment of the present invention are known to those skilled in the art and will not be described in detail herein.

According to the utility model discloses indirect heating equipment of second aspect embodiment, include according to the utility model discloses the first aspect embodiment rotary compressor 1. For example, the heat exchange device can be an air conditioner, a refrigeration device and a heat pump water heater.

According to the utility model discloses indirect heating equipment utilizes rotary compressor 1 as above, lubricating oil and counter shaft counter weight mutually noninterfere, the vibration is little, wearing and tearing are little.

In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", and the like, indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for convenience of description and simplicity of description, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore, should not be construed as limiting the present invention.

Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, 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 unless otherwise specified.

In the description of the present invention, "first feature" and "second feature" may include one or more of the features, and the first feature may be "on" or "under" the second feature, and may include the first and second features being in direct contact, or the first and second features being in contact not directly but via another feature therebetween. The first feature being "on," "over" and "above" the second feature includes the first feature being directly on and obliquely above the second feature, or merely indicating that the first feature is at a higher level than the second feature.

It is to be noted that, in the description of the present invention, unless otherwise explicitly specified or limited, the terms "mounted", "connected" and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; either directly or indirectly through intervening media, or through the communication between two elements. The specific meaning of the above terms in the present invention can be understood in specific cases to those skilled in the art.

In the description herein, references to the description of the term "one embodiment," "some embodiments," "a specific embodiment," "an example" or "some examples" or the like are intended to mean 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.

While embodiments of the present invention have been shown and described, it will be understood by those of ordinary skill in the art that: various changes, modifications, substitutions and alterations can be made to the embodiments without departing from the principles and spirit of the invention, the scope of which 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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