JPH04252892A - Rotary compressor - Google Patents

Abstract

PURPOSE:To disuse the conventional reed valve and improve the extent of compression efficiency in preventing any overcompression in a cylinder bore from occurring as well as to restrain a valve crack and a valve noise from occurring. CONSTITUTION:A rotary valve 6, which is provided with an interconnecting part 61 being interconnected to a discharge part 38 opening a discharge port 38a to a discharge space 5, and a closing part 62 closing the former, is installed in a discharge port part 38 of a compression element 3. This rotary valve 6 is interlocked to a driving shaft 4 so as to make the interconnecting part 61 interconnect the port 38a and the discharge part 38b in the discharge angle range of a roller 34, and in the desired discharge angle range, the discharge port 38a is forcibly opened to the discharge part 38b, thus discharge takes place without any overcompression.

Description

[Detailed description of the invention]

0001

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary compressor, and more particularly to a discharge structure for compressed gas refrigerant compressed within a cylinder bore of a compression element.

0002

BACKGROUND OF THE INVENTION Conventionally, this type of rotary compressor is described in, for example, Japanese Patent Laid-Open No. 176678/1983, and
As shown in FIG. 9, a motor B is disposed inside a sealed casing A, and a compression element D that is rotationally driven by a drive shaft C extending from the motor B is disposed below the motor B. The compression element D includes a cylinder E having a cylinder bore a, front and rear heads F and G having face surfaces that close the bore a, and a compression element D disposed within the bore a and connected to the drive shaft C. It consists of a roller H into which the eccentric shaft part b is inserted. In addition, the front and rear heads F, G are provided with discharge ports I, I, respectively, which open into the bore a, and each discharge port I is provided with a reed valve J.
, J are provided respectively. Then, the drive shaft C is rotated by the drive of the motor B, and the roller H is eccentrically rotated within the bore a of the cylinder E by the eccentric shaft portion b of the drive shaft C, so that the gas is sucked into the bore a. When the refrigerant is compressed and the pressure in the compression chamber reaches a set pressure, each reed valve J is opened by the pressure in the compression chamber, and a discharge is formed from each discharge port I to the lower side of the motor B. Space K
compressed gas refrigerant is discharged. In the figure, L indicates a muffler fitted over the front and rear heads F and G.

0003

[Problem to be solved by the invention] However, as mentioned above,
In the configuration in which each reed valve J is provided at each discharge port I, since the responsiveness of each reed valve J is poor, especially when used in a high speed rotation range, as shown in FIG. The pressure in the room exceeds the predetermined set pressure and overcompresses (
(shaded area in the same figure), leading to a decrease in compression efficiency,
There have been problems in that valve sounds are generated as the reed valves J open and close, causing noise, and that the reed valves J may crack.

The present invention has been made in view of the above-mentioned problems, and its purpose is to eliminate overcompression due to the response delay of the reed valve by eliminating the reed valve, and to improve compression efficiency. To provide a rotary compressor that can eliminate valve cracking and valve noise.

[0005]

[Means for Solving the Problems] In order to achieve the above object, the present invention includes a cylinder bore 30, a roller 34 that rotates eccentrically within the cylinder bore 30, and a discharge port portion 38.
In a rotary compressor including a compression element 3 having a compression element 3 and a drive shaft 4 for driving the roller 34, a discharge port 38b of the compression element 3 is provided with a discharge port 38a opening into the discharge space 5. a communication portion 61 that communicates with the
A rotary valve 6 having a closing portion 62 to be closed is provided, and the rotary valve 6 is connected to the drive shaft 4, and the communication portion 61 communicates the port 38a and the discharge portion 38b within the discharge angle range of the roller 34. It is characterized by being linked together so that

Further, a port portion 38 having a circular inner peripheral surface and a discharge port 38a opening into the cylinder bore 30 is provided at the end of the compression stroke of the roller 34 in the cylinder 31 of the compression element 3. The port portion 38 is provided on one of the front head 32 and the rear head 33.
A discharge portion 38b communicating with the discharge space 5 and opening into the discharge space 5 is provided,
A rotary valve 6 having a circular outer circumferential surface 63 and a communication groove 64 and opening and closing the discharge port 38a may be rotatably installed in the port portion 38.

[0007]

[Operation] The roller 3 rotated within the cylinder bore 30
When the contact point 4 passes through the suction port and is in the initial stage of the compression stroke, the discharge port section 38 is closed by the closing section 62 of the rotary valve 6, which is rotated in conjunction with the drive shaft 4. Accordingly, the inside of the cylinder bore 30 is held in a closed state, and the gas refrigerant is compressed within the bore 30. When the pressure in the compression chamber reaches the discharge angle of the roller 34 at which the set pressure is reached, the communication portion 61 of the rotary valve 6 opens the discharge port portion 38 as the drive shaft 4 rotates, and the The gas refrigerant compressed in the bore 30 starts to be discharged into the discharge space 5, and the rotary valve 6 opens the discharge port 38 at a discharge angle from the discharge angle of the roller 34 to the completion of discharge. carried out over a range of
When this discharge angle range is exceeded, the rotary valve 6 stops opening the discharge port portion 38, and the discharge stroke ends. As described above, the discharge port 38 is forcibly opened and closed by the rotation of the rotary valve 6 interlocked with the drive shaft 4 without using a conventional reed valve, and the compressed air is compressed in the cylinder bore 30. Since the gas refrigerant can be discharged, the conventional reed valve can be omitted, and the compression efficiency is improved without overcompression caused by the response delay that occurs when using a reed valve. It is possible to improve the performance of the valve, and also eliminate the occurrence of valve cracking and valve sounds.

Further, a port portion 38 having a circular inner circumferential surface and a discharge port 38a opening into the cylinder bore 30 is provided at the end of the compression stroke of the roller 34 in the cylinder 31 of the compression element 3. A discharge part 38b communicating with the port part 38 and opening into the discharge space 5 is provided on one side of the front and rear heads 32, 33, and the port part 38 has a circular outer peripheral surface 63 and a communication groove 64, When rotatably installing the rotary valve 6 that opens and closes the discharge port 38a, as in the above case,
The occurrence of overcompression, valve cracking, and valve noise can be eliminated, and since the port portion 38 is provided at the compression end portion of the cylinder bore 30, the discharge port 3
The top clearance at 8a can be reduced, and compression efficiency can be increased.

[0009]

[Embodiment] The rotary compressor shown in FIGS. 1 and 2 has a stator 21 and a rotor 22 at the inner upper part of a hermetic casing 1.
A compression element 3 is disposed on the lower side of the motor 2, and this compression element 3 is
It is composed of a cylinder 31 having a cylinder bore 30 therein, front and rear heads 32 and 33 having faces that close the upper and lower portions of the bore 30, and a roller 34 disposed within the bore 30. Further, a drive shaft 4 having an eccentric shaft portion 41 is connected to the rotor 22 of the motor 2, and the upper and lower portions of the eccentric shaft portion 41 of the drive shaft 4 are connected to the center upper and lower portions of the front and rear heads 32, 33. Bearings are supported by the protruding boss portions 35, 35, and the eccentric shaft portion 41 of the drive shaft 4 is inserted into the roller 34 in the bore 30, and the cylinder 31 is in constant contact with the roller 34. A suction port 37 and a discharge port portion 38 are provided near the vane 36 at forward and backward positions in the rotational direction of the roller 34.
A suction chamber and a compression chamber are respectively defined between the vane 36 and the contact point of the roller 34 with respect to the inner wall surface of the bore 30, so that the eccentric rotation of the eccentric shaft portion 41 While moving the contact point, the roller 34 is moved into the cylinder bore 30.
By rotating the gas refrigerant in the suction chamber from the suction port 37 of the cylinder 31, the gas refrigerant is compressed in the compression chamber, and at the compression end position of the roller 34, the gas refrigerant is transferred from the discharge port portion 38 to the inside of the casing 1. The liquid is discharged into a discharge space 5 formed on the lower side of the motor 2.

[0010] Therefore, the discharge structure of the compressed gas refrigerant in the rotary compressor is constructed as follows. That is, the discharge port portion 38 of the compression element 3 is provided with a discharge port 38a that opens to the cylinder bore 30 and a discharge portion 38b that opens to the discharge space 5,
The discharge port portion 38 includes a communication portion 61 that communicates the discharge port 38a with the discharge portion 38b, and the discharge port 3.
8a and a closing part 62 for closing between the discharge part 38b. Port 38a and discharge part 3
8b so as to communicate with each other.

Specifically, as shown in FIGS. 1 and 2, a discharge port portion 38 having a circular inner circumferential surface and a predetermined height is formed at the end of the compression stroke of the roller 34 in the cylinder bore 30. Then, a cylinder bore 30 is provided at a portion of the discharge port portion 38 facing the cylinder bore 30.
The discharge port 38a is opened to communicate the compression chamber of the front head 32 with the discharge port section 38.
The discharge portion 38b, which communicates with the discharge port portion 38 and opens into the discharge space 5, is formed at a position opposite to the discharge port portion 38 in . Then, the discharge port section 38
The rotary valve 6 is rotatably disposed within the discharge port section 3.
It has a cylindrical shape with a circular outer circumferential surface 63 whose diameter is slightly smaller than the circular inner circumferential surface of No. By opening in the vertical direction from the edge to the upper end edge of the cylinder 31, a communication groove 64 as the communication part 61 is formed, and a portion other than the communication groove 64 closes the discharge port 38a. 62.

Further, the rotary valve 6 is rotated in synchronization with the drive shaft 4. That is, the rotary valve 6 is provided with a rotating shaft 7, and the rotating shaft 7 protrudes from the rear head 33. A first gear 8 is provided at the lower end, and the first gear 8 is provided at the lower end of the drive shaft 4.
The second gear 9 meshing with the first and second gears is fixed, and
The rotary valve 6 is synchronized with the drive shaft 4 through the gears 8 and 9 so that the communication groove 64 allows the port 38a and the discharge portion 38b to communicate with each other within the discharge angle range of the roller 34.

Next, the operation of the above structure will be explained based on FIGS. 3 to 7. FIG. 3 shows a state where the rotation angle of the roller 34 in the cylinder bore 30 is 0 degrees, that is, the contact point of the roller 34 with respect to the inner wall of the bore 30 faces the vane 36 as shown in FIG. FIG. 4 shows the position of the rotary valve 6 when discharge from the compression chamber is completed in the previous stroke, and FIG.
When the rotation angle of the roller 34 within is 90 degrees,
In other words, FIG. 5 shows the position of the rotary valve 6 when the contact point is moved 90 degrees beyond the suction port 37 from the state shown in FIG. The position of the rotary valve 6 when the contact point is moved 180 degrees from the state shown in FIG. 3 is also shown in FIG.
7 shows the position of the rotary valve 6 when the rotation angle of the roller 34 in the bore 30 is 200 degrees, that is, when the contact point is moved 200 degrees from the state in FIG. The positions of the rotary valve 6 are shown when the rotation angle of the roller 34 in the roller 30 is 270 degrees, that is, when the contact point is moved 270 degrees from the state of FIG.

First, the rotation angle of the roller 34 is 0 degrees (
In the range of 180 degrees (state in Figure 2), that is,
In the range in which the contact point of the roller 34 with respect to the bore 30 is rotated 180 degrees from the opposite position of the vane 36 through the suction port 37, the compression in the compression chamber is below the set pressure; In some cases, the closing portion 62 of the rotary valve 6, which is rotated in synchronization with the drive shaft 4, is rotated to the side of the discharge port 38a of the discharge port portion 38, and the closing portion 62 of the rotary valve 6 is rotated to the side of the discharge port 38a of the discharge port portion 38.
and the discharge portion 38b, the bore 3
0 is maintained in a closed state, and the gas refrigerant is compressed within the compression chamber. When the rotation angle of the roller 34 reaches 200 degrees (the state shown in FIG. 6), that is, when the pressure in the compression chamber reaches the set pressure, the rotary valve 6 rotates in synchronization with the drive shaft 4. The communication groove 64 is rotated to the opening position of the discharge port 38a of the discharge port portion 38, and the discharge port 38a and the discharge portion 38b are communicated via the communication groove 64, and the inside of the compression chamber of the cylinder bore 30 is opened. Discharge of the compressed gas refrigerant into the discharge space 5 is started, and the discharge angle (200
The communication groove 64 connects the discharge port 38a and the discharge part 38b in the discharge angle range from
The compressed gas refrigerant continues to be discharged into the discharge space 5. That is, the closing portion 62 of the rotary valve 6 is connected to the discharge port 38a of the discharge port portion 38.
The discharge stroke is completed when the valve is closed.

As described above, the rotary valve 6 which rotates in synchronization with the drive shaft 4 is used to control the discharge port portion 38.
Since the compressed gas refrigerant compressed in the compression chamber can be discharged by forcibly opening and closing the reed, the reed can be discharged within a desired discharge angle range without using a conventional reed valve. It is possible to prevent the occurrence of overcompression, valve cracking, valve noise, etc. as in the case of using a valve, and in addition, the discharge port portion 38 is provided at the compression end portion of the cylinder bore 30, and this discharge port portion 3
8 is provided with the rotary valve 6 for opening and closing the discharge port 38a, the top clearance at the discharge port 38a can be reduced and compression efficiency can be increased.

Furthermore, in the present invention, as shown in FIG.
The discharge port portion 38 is formed on the front head 32 side constituting the compression element 3, and the discharge port 38 is formed in a part of the upper edge of the cylinder 31 and communicates with the inside of the cylinder bore 30.
8a, and a discharge portion 38b opened to the discharge space 5 on the upper surface side of the front head 32,
The discharge port section 38 is provided with a communication groove 64 as a communication section 61 for communicating the discharge port 38a with the discharge section 38b, and a closing section 62 for closing between the discharge port 38a and the discharge section 38b. A rotary valve 6 is provided, and the rotary valve 6 is synchronized with the drive shaft 4 so that the communication groove 64 communicates the discharge port 38a and the discharge portion 38b over the discharge angle range of the roller 34. may be configured. In this case, as in the case described above, the rotating shaft 7 of the rotary valve 6 is provided with a first gear 8 that meshes with the second gear 9 provided on the drive shaft 4 side, and each of these gears 8, 9, the rotary valve 6 is synchronized with the drive shaft 4.

In the above embodiment, the front head 3
Although the discharge part 38b of the discharge port part 38 is provided on the second side, in the present invention, the discharge part 38b of the discharge port part 38 is provided on the rear head 33 side.
b may also be established. Further, in the embodiment described above, the rotary valve 6 is communicated with the roller 34 at a rotation angle of 200 degrees, but this angle is arbitrary and cannot be changed by changing the setting pressure of the discharge pressure. be.

[0018]

As explained above, in the rotary compressor of the present invention, the discharge port portion 38 of the compression element 3 is provided with the discharge port 38a that opens into the cylinder bore 30.
A rotary valve 6 is provided which has a communication part 61 that communicates with the discharge part 38b that opens to the discharge part 38b, and a closing part 62 that closes the rotary valve 6. Port 3 in range
8a and the discharge portion 38b are linked to communicate with each other, the conventional reed valve can be eliminated, and the discharge port 38a can be forcibly communicated with the discharge portion 38b for discharge in a desired discharge angle range. This makes it possible to prevent overcompression from occurring within the cylinder bore 30 and improve compression efficiency, unlike the conventional method using the reed valve, and also to eliminate valve cracking and valve noise.

Further, a port portion 38 having a circular inner circumferential surface and a discharge port 38a opening into the cylinder bore 30 is provided at the end of the compression stroke of the roller 34 in the cylinder 31 of the compression element 3. A discharge part 38b communicating with the port part 38 and opening into the discharge space 5 is provided on one side of the front and rear heads 32, 33, and the port part 38 has a circular outer peripheral surface 63 and a communication groove 64, By rotatably incorporating the rotary valve 6 that opens and closes the discharge port 38a, it is possible to eliminate the occurrence of overcompression, valve cracking, and valve noise, as in the case described above, and, moreover, the The top clearance can be reduced and compression efficiency can be increased.

[Brief explanation of the drawing]

FIG. 1 is a partially omitted sectional view of a rotary compressor according to the present invention.

FIG. 2 is a cross-sectional plan view of the main parts of the rotary compressor.

FIG. 3 is a plan cross-sectional view of the main parts of the rotary compressor illustrating an operating state (rotation angle of 0 degrees).

[Figure 4] Operating state of the same rotary compressor (rotation angle 90
FIG.

[Figure 5] Operating status of the same rotary compressor (rotation angle 18
0 degree) is a plan sectional view of the main part.

[Figure 6] Operating state of the same rotary compressor (rotation angle 20
0 degree) is a plan sectional view of the main part.

[Figure 7] Operating state of the same rotary compressor (rotation angle 27
0 degree) is a plan sectional view of the main part.

FIG. 8 is a sectional view showing another embodiment.

FIG. 9 is a partially omitted cross-sectional view showing a conventional rotary compressor.

FIG. 10 is a diagram illustrating the compression characteristics of the rotary compressor.

[Explanation of symbols]

3 Compression element 30 Cylinder bore 31 Cylinder 32 Front head 33 Rear head 34 Roller 38 Discharge port section 38a Discharge port 38b Discharge part 4 Drive shaft 5 Discharge space 6 Rotary valve 61 Communication part 62 Closed part 63　Circular outer peripheral surface 64 Communication groove

Claims (2)

[Claims] Claim 1: A cylinder bore 30, a roller 34 that rotates eccentrically within the cylinder bore 30, and a discharge port portion 3.
8, and a drive shaft 4 that drives the roller 34, the discharge port 38 of the compression element 3 has a discharge port 38a that opens into the discharge space 5. A rotary valve 6 having a communication portion 61 that communicates with the drive shaft 4 and a closing portion 62 that closes the rotary valve 6 is provided.
The rotary compressor is characterized in that the communication portion 61 is interlocked to communicate the port 38a and the discharge portion 38b within a discharge angle range of the roller 34. 2. A port portion 38 having a circular inner circumferential surface and a discharge port 38a opening into the cylinder bore 30 is provided at the end of the compression stroke of the roller 34 in the cylinder 31 of the compression element 3. head 32
and a discharge part 38b that communicates with the port part 38 and opens into the discharge space 5 is provided on one side of the rear head 33, and the port part 38 has a circular outer peripheral surface 63 and a communication groove 64,
The rotary compressor according to claim 1, further comprising a rotatable internal rotary valve 6 for opening and closing the discharge port 38a.