CN111749892A

CN111749892A - Rotor type compressor

Info

Publication number: CN111749892A
Application number: CN201910246168.3A
Authority: CN
Inventors: 匡勇军
Original assignee: Shanghai Highly Electrical Appliances Co Ltd
Current assignee: Shanghai Highly Electrical Appliances Co Ltd
Priority date: 2019-03-29
Filing date: 2019-03-29
Publication date: 2020-10-09

Abstract

The invention provides a rotor type compressor, and belongs to the technical field of compressors. The rotor compressor comprises a shell, a motor and a pump body part, wherein the pump body part comprises a cylinder, a crankshaft, an upper cylinder cover and a lower cylinder cover; the exhaust valve comprises a valve seat, an impeller and a ratchet wheel; an inner cavity is arranged in the valve seat, the impeller is provided with a plurality of blades, and a partition cavity is formed between the blades; the impeller realizes unidirectional rotation towards a preset direction through a ratchet wheel; the valve seat is provided with a suction inlet and a discharge outlet which are communicated with the inner cavity, and when the pressure in the suction inlet is greater than the pressure in the discharge outlet, the gas or/and liquid entering the partitioned cavity between the blades is transmitted to the discharge outlet from the suction inlet through the rotation of the impeller; the suction inlet of the exhaust valve is communicated with the exhaust port of the cylinder. The exhaust valve has the advantages that the valve plate and the baffle or the seat ring cannot collide when the exhaust valve works, so that the reliability of the exhaust valve is improved, and the noise of the compressor is reduced.

Description

Rotor type compressor

Technical Field

The invention relates to the technical field of compressors, in particular to a rotor type compressor.

Background

The rotor compressor is widely used in electrical equipment such as air conditioners, refrigerators and the like, and the volumetric efficiency of the compressor is one of the main parameters for evaluating the performance of the compressor.

The exhaust valve in the current rotary compressor usually adopts a reed valve structure, which is usually shown in fig. 1 and comprises a bolt or rivet 1, a baffle 2, a valve plate 3, a seat ring 4 and a valve seat 5, wherein the seat ring 4 is usually made of powder metallurgy material and then pressed into and penetrates through the valve seat 5, or the valve seat 5 and the seat ring 4 are directly milled into an integral structure by utilizing cast iron material of the valve seat 5.

However, the conventional rotary compressor has at least the following problems: because the rotor type compressor contains the reed valve structure, the valve block of reed valve structure frequently strikes with baffle and seat circle, leads to the noise great to the reliability of reed valve structure is relatively poor.

Disclosure of Invention

The invention provides a rotor type compressor, which is used for reducing the noise of the rotor type compressor and improving the reliability of an exhaust valve.

In order to achieve the purpose, the invention provides a rotor type compressor, which comprises a shell, a motor and a pump body part, wherein the pump body part comprises a cylinder, a crankshaft, an upper cylinder cover and a lower cylinder cover;

the exhaust valve comprises a valve seat, an impeller and a ratchet wheel;

an inner cavity for accommodating the impeller is arranged in the valve seat, the impeller is provided with a plurality of blades, and a partition cavity is formed between the blades;

the impeller realizes unidirectional rotation towards a preset direction through the ratchet wheel;

the valve seat is provided with a suction inlet and a discharge outlet which are communicated with the inner cavity, and when pressure difference exists between two sides of an impeller in the valve seat and the pressure in the suction inlet is greater than the pressure in the discharge outlet, gas or/and liquid entering a cavity divided between the blades is transmitted to the discharge outlet from the suction inlet through the rotation of the impeller; when the pressure in the suction port is smaller than the pressure in the discharge port, the ratchet wheel limits the impeller to rotate reversely;

the exhaust valve is arranged in the body of the cylinder or the body of the cylinder cover, a suction inlet of the exhaust valve is communicated with an exhaust port of the cylinder, and a discharge outlet of the exhaust valve is communicated with the inner cavity of the shell.

Optionally, the number n of the cylinders is greater than or equal to 2, an intermediate plate is arranged between adjacent cylinders, and the exhaust valve is arranged in the body of the intermediate plate.

Optionally, the shape of the inner cavity of the valve seat for accommodating the impeller is matched with the shape of the impeller, and the impeller is arranged in the inner cavity and forms a throttling sealing structure with the inner wall of the inner cavity through clearance fit.

Optionally, the impeller further has a wheel shaft and 2 circular baffles, the blades are uniformly distributed around the wheel shaft, and the 2 circular baffles are symmetrically connected to two sides of each blade in a direction perpendicular to the axial direction of the wheel shaft.

Optionally, the number of the blades included in the impeller is not less than 4.

Optionally, the suction channel corresponding to the suction inlet and the discharge channel corresponding to the discharge outlet are located on the same straight line.

Optionally, the cylinder includes a slide groove, and an included angle k between the mounting position of the exhaust valve and the slide groove is greater than or equal to 270 degrees and less than or equal to 360 degrees.

Optionally, the cylinder exhaust port is a kidney-shaped port, a circular port or a square port.

Optionally, the exhaust valve is cylindrical in shape.

Optionally, the ratchet is a friction type ratchet, an external tooth type ratchet or an internal tooth type ratchet.

Compared with the existing exhaust valve, the exhaust valve of the rotor compressor provided by the invention has the advantages that the exhaust valve is composed of the impeller, and the impact of a valve plate and a baffle or a seat ring cannot occur when the exhaust valve works, so that the reliability of the exhaust valve is improved, and the noise of the compressor is reduced.

Drawings

FIG. 1 is a schematic view of a prior art vent valve;

FIG. 2 is a schematic structural diagram of an exhaust valve installed in a cylinder body according to an embodiment of the present invention

FIG. 3 is a simplified cross-sectional view of FIG. 2;

FIG. 4 is a schematic structural view of a discharge valve according to an embodiment of the present invention;

FIG. 5 is a sectional view A-A of FIG. 4;

FIG. 6 is a schematic structural view of an exhaust valve installed in a body of a cylinder head according to an embodiment of the present invention;

FIG. 7 is a simplified right side view of FIG. 6;

fig. 8 is a schematic structural diagram of a throttling sealing structure according to an embodiment of the present invention.

[ reference numerals are described below ]:

1-bolts or rivets;

2-a baffle plate;

3, valve plates;

4-a seat ring;

5-valve seat;

21-cylinder; 22-a venting valve; 23-a clamp spring;

221-a valve seat;

222-an impeller;

223-ratchet wheel;

224-suction inlet;

225-exhaust port;

226-axle;

227-center line;

228-an end cap;

61-cylinder cover; 62-reinforcing plate.

Detailed Description

To make the objects, advantages and features of the present invention more apparent, a rotary compressor according to the present invention will be described in further detail with reference to the accompanying drawings. It is to be noted that the drawings are in a very simplified form and are not to precise scale, which is merely for the purpose of facilitating and distinctly claiming the embodiments of the present invention.

The embodiment of the invention provides a rotor compressor, which comprises a shell, a motor and a pump body part, wherein the shell is positioned outside the motor and the pump body, the pump body part comprises a cylinder, a crankshaft, an upper cylinder cover and a lower cylinder cover, the cylinder, the upper cylinder cover or/and the lower cylinder cover are/is provided with a cylinder exhaust port, the cylinder exhaust port is provided with an exhaust valve, referring to fig. 2 and 6, the cylinder exhaust port is provided with an exhaust valve 22, a suction inlet of the exhaust valve 22 is communicated with the cylinder exhaust port, a discharge port of the exhaust valve 22 is communicated with an inner cavity of the shell, and the cylinder 21 exhausts gas or/and liquid in the cylinder 21 through the exhaust valve 22;

optionally, the exhaust valve 22 is built into the body of the cylinder 21 or the body of the cylinder head 61;

optionally, in order to increase the exhaust effect, an included angle k between the mounting position of the exhaust valve and a vane slot of the compressor is generally set to be 270 ° ≦ k ≦ 360 °, where the included angle k is as shown in fig. 2, and an angle formed between the vane slot located right above and the exhaust valve in the counterclockwise direction satisfies 270 ° ≦ k ≦ 360 °; preferably, the included angle k can be set to be more than or equal to 340 degrees and less than or equal to 360 degrees;

the included angle condition of the exhaust valve when the exhaust valve is arranged on the cylinder cover is the same as the included angle condition of the exhaust valve arranged on the cylinder, namely the installation position of the corresponding exhaust valve is determined at the projection position of the middle plate on the cylinder after the cylinder cover and the cylinder are installed and matched; referring to fig. 6 and 7, the exhaust valve 22 is built in the body of the cylinder head 61, and a reinforcement plate 62 may be installed on an upper surface of the exhaust valve 22 in order to reinforce the exhaust valve 22;

referring to fig. 4 and 5, the exhaust valve 22 according to the embodiment of the present invention is shown, and the exhaust valve 22 includes a valve seat 221, an impeller 222, and a ratchet 223; the valve seat 221 is provided with an inner cavity with a shape matched with that of the impeller 222, the impeller 222 is arranged in the inner cavity and forms a throttling sealing structure with the inner wall of the inner cavity through clearance fit, the middle part of the impeller 222 is provided with an axle 226, the axle 226 is provided with a ratchet 223, and the impeller 222 can realize unidirectional rotation in the inner cavity towards a preset direction through the ratchet 223; wherein the ratchet 223 may be a friction type ratchet, an external tooth type ratchet or an internal tooth type ratchet. The valve seat 221 is provided with a suction port 224 and a discharge port 225 which are communicated with the inner cavity, and when the pressure of the suction port 224 is greater than that of the discharge port 225, the refrigerant drives the impeller 222 to rotate in a single direction in a preset direction, so that the refrigerant flows from the suction port 224 to the discharge port 225; when the pressure of suction port 224 is less than or equal to the pressure of discharge port 225, ratchet 223 stops impeller 222 from rotating.

Compared with the existing exhaust valve, the exhaust valve provided by the embodiment of the invention has the advantages that the condition that the valve plate 3 collides with the baffle 2 or the seat ring 4 cannot occur during the working process, so that the reliability of the exhaust valve is improved, and the noise of the compressor is reduced. In addition, the exhaust valve is integrated, so that the installation and the replacement are convenient; the exhaust valve does not need a baffle plate and a valve plate, the valve seat can not be made into an invagination thin-wall structure, and the deformation of the valve seat caused by riveting the baffle plate and the valve plate on the valve seat can be reduced.

Alternatively, the exhaust valve 22 may be shaped as a cylinder, with the exhaust valve 22 being mounted as a separate component in the body of the cylinder or in the body of the cylinder head. In other embodiments, the exhaust valve 22 may be made into a rectangular parallelepiped or other shapes according to actual needs.

Optionally, when the number n of the cylinders of the rotor compressor is greater than or equal to 2, an intermediate plate is arranged between adjacent cylinders, and an exhaust valve is arranged in the body of the intermediate plate. The included angle condition when the exhaust valve is installed on the middle plate is the same as the included angle condition installed on the air cylinder, namely the installation position of the corresponding exhaust valve is determined according to the projection position of the middle plate on the air cylinder, and the air cylinder can exhaust gas or/and liquid through the exhaust valve in the middle plate.

According to the rotor compressor provided by the embodiment of the invention, the exhaust valve is arranged in the body of the middle plate in a built-in mounting mode, so that the exhaust valve can be conveniently mounted and replaced.

Optionally, the exhaust port of the cylinder is a kidney-shaped hole, a circular hole or a square hole, and the suction port 224 and the exhaust port 225 of the exhaust valve 22 are provided with a kidney-shaped hole, a circular hole or a square hole matched with the exhaust port of the cylinder. As shown in fig. 3, the discharge port 225 is a square port to increase the flow area of the refrigerant, whereas the discharge valve of the prior art is limited by the valve plate and the sealing performance, and the suction port and the discharge port are generally only circular ports.

Optionally, the rotor compressor further comprises a clamp spring, the clamp spring is located at two ends of the exhaust valve, and the clamp spring axially positions the exhaust valve. Referring to fig. 3, snap springs 23 may be installed at both ends of the discharge valve 22, respectively, to further fix the discharge valve 22.

Optionally, the rotor compressor further includes a dowel pin for fixing the discharge valve 22. In order to further fix the exhaust valve 22, a dowel pin may be installed at a contact surface position of the exhaust valve 22 and the cylinder 21, and similarly, a dowel pin may be installed at a contact surface position of the exhaust valve 22 and the intermediate plate.

Optionally, the impeller 222 has 2 circular baffles and a plurality of blades, each blade is located between the 2 circular baffles, and adjacent blades and the circular baffles form a chamber for conveying the refrigerant. Wherein, the blades and the circular baffle can be assembled together or integrally formed; the shape of 2 circular baffles is matched with the shape of the inner cavity of the valve seat 221, the adjacent blades and the circular baffles form a chamber, the chamber is used for transmitting a refrigerant, the distance between one end of each blade, which is far away from the axle center of the impeller 222, and the inner wall of the inner cavity of the valve seat 221 is very small, so that each chamber and the inner wall of the inner cavity of the valve seat 221 form a throttling sealing structure, when a refrigerant enters the suction port 224, the pressure of the refrigerant at the suction port 224 is greater than that of the refrigerant at the discharge port 225, the thrust of the refrigerant on the impeller 222 and the control direction of the ratchet 223 are in the same direction, and the impeller 222 is further driven to rotate; when the refrigerant pressure of the suction port 224 is smaller than the refrigerant pressure of the discharge port 225, the thrust of the refrigerant to the impeller 222 is opposite to the control direction of the ratchet 223 at the moment, and the impeller 222 stops rotating; when the pressure of the refrigerant at the suction port 224 is equal to the pressure of the refrigerant at the discharge port 225, the impeller 222 is balanced in force at both sides, and the impeller 222 does not rotate.

In other embodiments, when the circular baffles are not disposed on both sides of the vane, the adjacent vanes and the inner wall of the inner cavity of the valve seat 221 form chambers, the distance between the periphery of each vane and the inner wall of the inner cavity of the valve seat 221 is small, and the chambers and the inner wall of the inner cavity of the valve seat 221 can also form a throttling sealing structure. However, the sealing effect between the impeller and the valve seat is poor compared with the sealing effect between the closed impeller and the valve seat at the upper section, and because small gaps exist between the circumferential direction and the two sides of the impeller and the inner wall of the inner cavity of the valve seat, the leakage amount of the refrigerant is large.

Alternatively, the suction passage corresponding to the suction port 224 and the discharge passage corresponding to the discharge port 225 are positioned on the same line. As shown in fig. 5, the suction channel and the discharge channel are disposed on the same straight line and on the same side of the center line 227, so that when the pressure of the suction port 224 is greater than the pressure of the discharge port 225, the refrigerant drives the impeller 222 to rotate in a single direction in a predetermined direction, and when the predetermined direction is shown in fig. 5, the refrigerant is transmitted from the suction port 224 to the discharge port 225 in a counterclockwise direction; when the pressure of the suction port 224 is less than or equal to the pressure of the discharge port 225, the impeller 222 is not rotated due to the ratchet 223 to prevent the refrigerant from flowing backward. In addition, the suction channel and the discharge channel are arranged on the same straight line, so that the production and the processing are convenient.

In other embodiments, the suction channel and the discharge channel may not be aligned, or the suction channel and the discharge channel may not be parallel to the center line 227, as long as the resultant force of the refrigerant entering from the suction port 224 to the impeller is the same as the preset direction, and the resultant force of the refrigerant returning from the discharge port 225 to the impeller is opposite to the preset direction, which is not limited in the present invention.

Optionally, the number m of the blades included in the impeller 222 satisfies that m is greater than or equal to 4. According to the labyrinth sealing principle, the sealing effect is related to the number of the chambers, and when the number of the chambers reaches a certain number, the sealing effect can be close to complete sealing. Based on the actual test results, when the number of chambers is 4, that is, the number of blades is 4, the sealing effect can reach about 92%, so in the present embodiment, the number m of chambers included in the impeller 222 is set to satisfy m ≧ 4. The distance between each blade and the inner wall of the base 221 is small, and the distance may be specifically set according to the material of the blade, the material of the base, and the expansion characteristic of the refrigerant, and generally, the minimum value e of the distance between the blade and the inner wall of the base 221 may be set to 0 < e < 3 mm, so that the impeller 222 and the base 221 form a throttle sealing structure, which may also be referred to as a labyrinth sealing structure.

The principle of the labyrinth seal structure is shown in fig. 8, which is divided into 5 regions, P0, P1, P2, P3 and P4, the pressure of the 5 regions when the refrigerant passes through the 5 regions is sequentially represented by P0, P1, P2, P3 and P4, assuming that the original pressure difference between the high pressure region P0 and the low pressure region P4 is y, when the refrigerant leaks from the high pressure region P0 to the low pressure region P4, the leakage amount is positively correlated with the gap a and the original pressure difference y, when a part of the refrigerant flows from P0 to the P1 space through the gap a, the refrigerant expands in the P1 region, the refrigerant pressure decreases, so that P1 < P0, and by analogy, the leakage amount of P4 < P3 < P2 < P1 < P0 is much smaller than that of the refrigerant directly leaks from the P0 region to the P4 region, thereby achieving the seal function.

When the pressure of the suction port 224 is greater than the pressure of the discharge port 225, the refrigerant drives the impeller 222 to rotate in a single direction towards a preset direction, so that the refrigerant is transmitted from the suction port 224 to the discharge port 225; when the pressure of the suction port 224 is less than or equal to the pressure of the discharge port 225, the impeller 222 does not rotate due to the ratchet 223, so as to prevent the refrigerant from flowing back; the impeller 222 forms a throttle seal structure with the valve seat 221, thereby further preventing the refrigerant from flowing back from the discharge port 225 to the suction port 224. The exhaust valve provided by the invention does not comprise a spring, so that the reliability of the exhaust valve is improved; in addition, the exhaust valve provided by the invention has no impact sound between the valve core and the valve seat, and reduces the noise generated when the exhaust valve works.

As can be seen from fig. 2, 4 and 5, the exhaust valve provided by the present invention realizes the transmission of the injected refrigerant gas or liquid through the rotation of the impeller, and the wheel axle in the middle of the impeller is provided with a ratchet structure, thereby realizing the unidirectional rotation of the impeller. When the injection is needed, the pressure difference exists between the two sides of the impeller in the exhaust valve, the suction side pressure is larger than the discharge side pressure, namely the pressure of the suction port 224 is larger than the pressure of the discharge port 225, and the refrigerant gas or liquid entering the dividing cavity between the blades of the impeller is transmitted from the suction side to the discharge side through the rotation of the impeller, so that the through flow of the refrigerant is realized. The flow rate of the refrigerant can be automatically adjusted through the rotating speed of the impeller according to the pressure difference. When the pressure difference is balanced, the impeller stops rotating; due to the ratchet, the impeller cannot rotate in the reverse direction when the suction-side pressure is less than the discharge-side pressure. Meanwhile, a throttling sealing structure is formed between the impeller partition cavity and the contour clearance of the valve seat, so that refrigerant gas or liquid can be effectively prevented from flowing back from the discharge side to the suction side, and the unidirectional exhaust effect is achieved.

Alternatively, the blades of the impeller 222 are evenly distributed on the impeller 222. The blades are uniformly arranged on the impeller 222, so that the size of the divided cavities among the blades can be equal, and when the impeller 222 rotates, the impeller 222 can rotate at a balanced rotating speed for the refrigerant with constant pressure because the volume of the refrigerant in each divided cavity is the same. In this embodiment and other embodiments, for the refrigerant with a varying pressure, the impeller 222 may automatically adjust its rotation speed to complete the refrigerant transmission depending on the pressure of the refrigerant.

Optionally, the valve seat 221 is composed of a plurality of split bodies, and each split body is provided with a positioning pin hole. The exhaust valve can be accurately positioned when being installed through the positioning pin holes.

Alternatively, the connection positions of the valve seat 221 and the valve body are connected by welding. When the exhaust valve is assembled, in order to enhance the sealing effect of the exhaust valve, the connection position between the components of the valve seat 221 may be welded, for example, the end cover 228 and the valve seat 221 in fig. 4 may be connected by welding.

The above description is only for the purpose of describing the preferred embodiments of the present invention, and is not intended to limit the scope of the present invention, and any variations and modifications made by those skilled in the art based on the above disclosure are within the scope of the claims of the present invention.

Claims

1. A rotor compressor comprises a shell, a motor and a pump body part, wherein the pump body part comprises a cylinder, a crankshaft, an upper cylinder cover and a lower cylinder cover;

the exhaust valve comprises a valve seat, an impeller and a ratchet wheel;

the suction inlet of the exhaust valve is communicated with the exhaust port of the cylinder, and the exhaust outlet of the exhaust valve is communicated with the inner cavity of the shell.

2. The compressor as claimed in claim 1, wherein the number n of the cylinders is greater than or equal to 2, an intermediate plate is disposed between adjacent cylinders, and the exhaust valve is disposed in a body of the intermediate plate.

3. The compressor of claim 1, wherein the valve seat has an inner cavity for receiving the impeller, the inner cavity having a shape matching the shape of the impeller, the impeller being disposed in the inner cavity and forming a throttling sealing structure with an inner wall of the inner cavity by clearance fit.

4. The compressor of claim 1, wherein the impeller further has a hub and 2 circular baffles, the plurality of blades are evenly distributed around the hub, and the 2 circular baffles are symmetrically connected to both sides of the blades perpendicular to an axial direction of the hub.

5. The compressor of claim 1, wherein said impeller includes a number of blades not less than 4.

6. The compressor of claim 1, wherein the suction passage corresponding to the suction port and the discharge passage corresponding to the discharge port are located on a same line.

7. The compressor of claim 1, wherein the cylinder includes a vane groove, and an angle k between a mounting position of the discharge valve and the vane groove satisfies 270 ° ≦ k ≦ 360 °.

8. The compressor of claim 1, wherein the cylinder exhaust port is a kidney port, a circular port, or a square port.

9. A compressor according to any one of claims 1 to 8, wherein said discharge valve is cylindrical in shape.

10. The compressor of claim 1, wherein the ratchet is a friction ratchet, an external tooth ratchet, or an internal tooth ratchet.