JPH04255592A - Rotary compressor - Google Patents

Abstract

PURPOSE:To prevent bounding friction at the time of sliding a blade so as to prevent a mechanical loss, and decrease of reliability due to the bounding friction by providing guide grooves of the blade, extended to face surfaces in a front and a rear head and a guide part, slid engaged with the guide groove, in the blade. CONSTITUTION:Guide grooves 52, 62, extended to face surfaces 51, 61, are provided in front/rear heads 5, 6. Guide parts 81, 82, slid engaged with the guide grooves 52, 62, are provided in a blade 8. A load of high pressure fluid, acting in an advancing part into a bore 41 of the blade 8, is supported by an engaging part of the guide part 81, 82, engaged with the guide grooves 52, 62, to prevent bounding friction of the blade 8 of advancing/retracting to/from in the bore 41. Volumetric efficiency can be also improved by decreasing leakage to a low pressure side of the high pressure fluid from upper/lower end parts of the blade 8 by a labyrinth effect in the engaging part.

Description

[Detailed description of the invention]

0001

[Industrial Field of Application] The present invention relates to a rotary compressor, and more particularly, an eccentrically rotating roller is installed in the bore of a cylinder, a blade is slidably supported in the cylinder and is in sliding contact with the outer peripheral surface of the roller. , relates to a rotary compressor provided with front and rear heads having face surfaces facing the bore.

0002

2. Description of the Related Art Conventionally, this type of rotary compressor is disclosed in, for example, Japanese Utility Model Application Publication No. 2-127793, and FIG.
As shown in , a cylinder B having a bore A is provided with a blade sliding groove D that slidably supports a blade C, and the tip of the blade C is rotated eccentrically in the direction of the arrow within the bore A. The blade C is brought into sliding contact with the bore A, and the blade C is moved back and forth into the bore A by eccentric rotation of the roller E. Further, in the configuration shown in FIG. 4, grooves F extending in the forward and backward directions of the blade C are provided on the upper and lower surfaces of the blade C, and the grooves F are provided in the front and rear heads disposed above and below the cylinder B. A protrusion G corresponding to F is provided to guide the blade C in the sliding direction. That is, when compressing gas in the cylinder B due to eccentric rotation of the rotor E, the bore A of the blade C
High pressure acts on the part that advances inward, and the load due to this high pressure is applied to the four contact points a to d shown by black dots in Figure 4.
The wear of the blade C and the blade sliding groove D caused by the advance and retreat of the blade C is reduced compared to a general type without the groove F and the protrusion G. Note that H is an eccentric shaft portion that drives the roller E.

0003

[Problems to be Solved by the Invention] However, even in the conventional example shown in FIG. 4, when a load due to high pressure is applied to the blade C, the blade C, when advanced into the bore A, has a cantilevered shape. For this reason, there was a problem that the boundary friction became large and the sliding resistance increased especially at the contact points a and c, causing wear and, in some cases, seizure. Further, since the upper and lower end surfaces of the protruding portion of the blade C into the bore A and the upper and lower end surfaces of the roller E only face the lower surface of the front head and the upper surface of the rear head, respectively, the roller E
When the fluid is compressed by the rotation of the blade C, high-pressure fluid leaks to the low-pressure side through the gaps between the upper and lower ends of the protruding portion of the blade C and the front and rear heads, and the gaps between the upper and lower ends of the roller E and the front and rear heads. As a result, there was a problem in that the volumetric efficiency of the rotary compressor was reduced due to this leakage.

The present invention was invented to solve the above problems, and its purpose is to enable the entire length of the blade to support the load caused by the high-pressure fluid acting on the portion of the blade that extends into the bore. The objective is to prevent boundary friction during blade sliding, and to prevent mechanical loss and reliability deterioration due to boundary friction.

Another object is to simultaneously reduce leakage from the compression chamber to the suction chamber and improve volumetric efficiency.

[0006]

[Means for Solving the Problems] In order to achieve the above object, in the present invention, a roller 7 that rotates eccentrically is installed in a bore 41 of a cylinder 4, and a blade that comes into sliding contact with the outer peripheral surface of the roller 7 is provided in the cylinder 4. The rotary compressor is provided with front and rear heads 5, 6 having face surfaces 51, 61 facing the bore 41, the front head and the rear head 5, 6 slidably supporting the rotary compressor.
, the blade 8 extending on the face surfaces 51 and 61;
guide grooves 52 and 62 are provided in the blade 8, and a guide portion 81 that engages with and slides in the guide grooves 52 and 62;
82 is provided.

[0007] Also, the face surface 5 of the guide grooves 52, 62
1 and 61 are located closer to the center of the bore 41 than the maximum eccentric position of the roller 7, and the guide portions 81 and 8
2 is preferably wrapped on the end face of the roller 7.

[0008]

[Operation] When compressing fluid by eccentrically rotating the roller 7 within the bore 41, the upper and lower guide portions 81 and 82 provided on the blade 8 slide while engaging with the guide grooves 52 and 62, respectively. However, the blade 8 has a guide groove 52,
62 into the bore 41. Therefore, when a load due to the pressure of the high-pressure fluid acts on the advancing portion of the blade 8 that has advanced into the bore 41, and the advancing portion is inclined toward the low pressure side around the inner circumferential wall of the bore 41. Since the blade 8 can be supported over the entire length of the engagement portion between the guide portions 81 and 82 and the guide grooves 52 and 62, when the blade 8 moves back and forth into the bore 41, the blade 8 Instead of tilting, it is received by the guide parts 81 and 82 and slides, so there is no boundary friction as in the conventional example.
Mechanical loss and reliability deterioration due to boundary friction can be prevented, and seizing of the blade 8 can also be prevented.

Furthermore, when the high-pressure fluid is about to leak to the low-pressure side through the upper and lower ends of the blade 8, the guide portions 81 and 82 are engaged with the guide grooves 52 and 62, respectively, so that the high-pressure fluid A so-called labyrinth effect is obtained in which the pressure flows toward the low pressure side along both side walls and the bottom wall of the guide grooves 52 and 62.
Moreover, since lubricating oil is present in the guide grooves 52 and 62, leakage of high-pressure fluid to the low-pressure side can be effectively reduced, and volumetric efficiency can be improved.

[0010] Also, the face surface 5 of the guide grooves 52, 62
1 and 61 is located closer to the center of the bore 41 than the maximum eccentric position of the roller 7, and the guide portion 81
, 82 wrap around the end surface of the roller 7, the tip of the blade 8 is rounded to reduce the sliding resistance between the tip of the blade 8 and the outer peripheral surface of the roller 7. Even when the blade 8 is in contact with the wires, high-pressure fluid can be prevented from leaking from around the roundness to the low-pressure side via the guide grooves 52 and 62. Therefore, even when the tip of the blade 8 is rounded, high-pressure fluid can leakage to the low-pressure side can be reduced, and volumetric efficiency can be improved.

[0011]

[Example] The rotary compressor shown in Fig. 3 has a closed case.
A motor 2 and a compression element 3 are disposed inside the thing 1, and the compression element 3 is connected to a drive shaft 21 extending from the motor 2.
I am trying to drive it by.

The compression element 3 has a cylinder 4 having a bore 41 and a blade sliding groove 42, and face surfaces 51 and 61 disposed on the upper and lower end surfaces of the cylinder 4 and facing the bore 41. front and rear heads 5, 6,
The blade 8 is slidably supported in the blade sliding groove 42, and the drive shaft 21 is connected to the roller 7.
An eccentric shaft portion 22 is inserted into the roller 7 so that the roller 7 is eccentrically rotated within the bore 41 by rotation of the drive shaft 21.

Further, the tip of the blade 8 is constantly biased on the outer peripheral surface of the roller 7 by a spring 83 provided behind the blade 8 and the pressure inside the casing 1 from which high-pressure fluid is released. The blade 8 is slid by the eccentric rotation of the roller 7, and the blade 8 is brought into contact with the roller 7.
The blade 8 always separates the high pressure side and the low pressure side during rotation.

[0014] However, what is shown in FIGS. 1 and 2 is
Guide grooves 52 and 62 for the blade 8 extending in the face surfaces 51 and 61 are provided in the front head 5 and the rear head 6, and the extended ends of these guide grooves 52 and 62 are arranged so that the maximum eccentricity of the roller 7 The bore 41 from the position
A guide portion 81 is located at the center side of the blade 8 and engages with the guide grooves 52 and 62 at the upper and lower ends of the blade 8.
, 82 are provided to connect the blade 8 and the guide portions 81, 82.
The overall height of the roller 7 is higher than that of the roller 7, and the engagement of the guide portions 81, 82 with the guide grooves 52, 62 causes the blade 8 moving back and forth into the bore 41 to move along the guide grooves 52, 62. The guide portions 81 and 82 are configured so that the guide portions 81 and 82 are guided in a straight line, and the tips of the guide portions 81 and 82 are always projected so as to overlap the upper and lower surfaces of the roller 7.

The lengths of the guide grooves 52 and 62 are such that when the roller 7 is located at the maximum eccentric position as shown in FIG. The length is such that there is a small gap between the groove ends of the guide grooves 52 and 62, so that the tip of the blade 8 can reliably come into contact with the outer peripheral surface of the roller 7.

Further, spring grooves 43 made of circular arcs having a diameter larger than the width of the blade 8 are provided on both side walls of the blade sliding groove 42, so that the spring 83 expands and contracts as the blade 8 slides. , so as not to come into contact with the side wall of the blade sliding groove 42 during expansion and contraction.

With the above configuration, when the drive shaft 21 is driven to rotate the roller 7 eccentrically and compress the fluid within the bore 41, the upper and lower guide portions 81 provided on the blade 8 , 82 are the guide grooves 52, 82, respectively.
By sliding while engaging with the guide grooves 62, the blade 8 moves back and forth into the bore 41 along the guide grooves 52, 62. At this time, a load due to the pressure of the high-pressure fluid acts in a cantilevered manner on the advanced portion of the blade 8 that has advanced into the bore 41, and the bore 41 of the blade 8 uses the inner circumferential wall of the bore 41 as a support point. An attempt is made to tilt the inward advancing portion toward the low pressure side, but at this time, the guide portion 81
, 82 and the guide grooves 52, 62, the blade 8 is not tilted when the blade 8 moves back and forth into the bore 41. The blade 8 slides while being received by the guide portions 81 and 82, and when the blade 8 moves back and forth into the bore 41 as the roller 7 rotates eccentrically, the blade 8 has the blade opening in the inner circumferential wall of the bore 41. Boundary friction does not occur between the opening side end of the sliding groove 42 and the low pressure side end as in the conventional example, and mechanical loss and reliability deterioration due to boundary friction can be prevented, and seizure can also be prevented. can do.

Furthermore, the high-pressure fluid compressed by the eccentric rotation of the roller 7 in the bore 41 of the cylinder 4 passes through the gaps between the front and rear heads 5 and 6 at the upper and lower ends of the blade 8 during compression. When leaking to the low pressure side, the guide portions 81 and 82 are engaged with the guide grooves 52 and 62, respectively, so that the high pressure fluid flows toward the low pressure side along the side walls and bottom wall of the guide grooves 52 and 62. Since the so-called labyrinth effect of flowing fluid is obtained and lubricating oil is present in the guide grooves 52 and 62, leakage of high-pressure fluid to the low-pressure side can be reduced, and volumetric efficiency can be improved.

Further, as shown in FIGS. 1 and 2, the tip of the blade 8 that slides on the outer peripheral surface of the roller 7 is rounded, so that the roller 7 and the blade 8 are in line contact. If the sliding resistance is reduced by
High pressure fluid flows from around the tip of the blade 8 into the guide groove 5.
2, 62 to the low pressure side, reducing the volumetric efficiency. By wrapping the tips of the guide portions 81 and 82 on the upper and lower surfaces of the roller 7, the tips of the guide portions 81 and 82 engage with the extended ends of the guide grooves 52 and 62, thereby closing the guide grooves 52 and 62. This can prevent high-pressure fluid from leaking to the low-pressure side from the guide grooves 52 and 62 at the tip of the blade 8. Therefore, blade 8
Even when the tip of the blade 8 is rounded in order to reduce the sliding resistance between the blade 8 and the roller 7, leakage of high-pressure fluid to the low-pressure side can be reduced, and the volumetric efficiency can be further improved. can be improved.

Furthermore, in the above embodiment, the guide portion 8
Although the widths of the guide grooves 52 and 82 are the same as the width of the blade 8, they may be made narrower. ，
The gap with the side wall of the bore 41 is made smaller than the gap between the side wall of the blade 8 and the side wall of the blade sliding groove 42 facing this side wall.
When a load due to the pressure of the high-pressure fluid acts on the protruding portion of the blade 8 that has protruded inward, the blade 8 is prevented from coming into contact with the low-pressure side end of the opening end on the bore 41 side of the blade sliding groove 42. This can be reliably prevented.

Furthermore, the guide portions 81 and 82 are connected to the blade 8.
It may be formed integrally with the blade 8, or it may be formed separately and fixed to the upper and lower ends of the blade 8.

[0022]

As explained above, in the present invention, the roller 7 that rotates eccentrically is installed in the bore 41 of the cylinder 4, and the blade 8 that comes into sliding contact with the outer peripheral surface of the roller 7 can be slid on the cylinder 4. The rotary compressor is provided with front and rear heads 5 and 6 having face surfaces 51 and 61 facing the bore 41 and supporting the rotary compressor.
, 61 are provided for the blade 8, and the blade 8 is provided with guide portions 81, 82 that engage and slide in the guide grooves 52, 62. When compressing fluid by eccentrically rotating the roller 7, the upper and lower guide portions 8 provided on the blade 8
1 and 82 slide while engaging with the guide grooves 52 and 62, respectively, and the blade 8 moves forward and backward into the bore 41 along the guide grooves 52 and 62. Therefore, a load due to the pressure of the high-pressure fluid acts in a cantilevered manner on the advanced portion of the blade 8 that has advanced into the bore 41, causing the advanced portion to tilt toward the low pressure side around the inner circumferential wall of the bore 41. Since the blade 8 can be supported over the entire length of the engagement portion between the guide portions 81 and 82 and the guide grooves 52 and 62, when the blade 8 is
1, the blade 8 does not tilt, but is received by the guide parts 81 and 82 and slides. Unlike the conventional example, boundary friction does not occur, and mechanical loss and mechanical loss due to boundary friction are eliminated. It is possible to prevent a decrease in reliability and also to prevent burn-in.

Furthermore, when the high-pressure fluid is about to leak to the low-pressure side through the upper and lower ends of the blade 8, the guide portions 81 and 82 are engaged with the guide grooves 52 and 62, respectively, so that the high-pressure fluid A so-called labyrinth effect is obtained in which the pressure flows toward the low pressure side along both side walls and the bottom wall of the guide grooves 52 and 62.
Furthermore, since lubricating oil is present in the guide grooves 52 and 62, leakage of high-pressure fluid to the low-pressure side can be effectively reduced, and volumetric efficiency can be improved.

Furthermore, the face surface 5 of the guide grooves 52 and 62
1 and 61 is located closer to the center of the bore 41 than the maximum eccentric position of the roller 7, and the guide portion 81
, 82 wrap around the end surface of the roller 7, the tip of the blade 8 is rounded to reduce the sliding resistance between the tip of the blade 8 and the outer peripheral surface of the roller 7. Even when the blade 8 is in contact with the wires, high-pressure fluid can be prevented from leaking from around the roundness to the low-pressure side via the guide grooves 52 and 62. Therefore, even when the tip of the blade 8 is rounded, high-pressure fluid can leakage to the low-pressure side can be reduced, and volumetric efficiency can be improved.

[Brief explanation of the drawing]

FIG. 1 is an enlarged partial cross-sectional view showing essential parts of the present invention.

FIG. 2 is a sectional view taken along line XX in FIG. 1;

FIG. 3 is a sectional view of a rotary compressor to which the present invention is applied.

FIG. 4 is a cross-sectional view showing a conventional example.

[Explanation of symbols]

4 Cylinder 5 Front head 6 Rear head 7 Roller 8 Blade 41 Boa 51, 61 Face surface 52, 62 Guide groove 81, 82 Guide part

Claims (2)

[Claims] 1. A roller 7 that rotates eccentrically is installed in a bore 41 of a cylinder 4, and a blade 8 that slides in contact with the outer peripheral surface of the roller 7 is slidably supported in the cylinder 4, and also faces the bore 41. A rotary compressor provided with front and rear heads 5 and 6 having face surfaces 51 and 61, the front and rear heads 5 and 6
, the blade 8 extending on the face surfaces 51 and 61;
guide grooves 52 and 62 are provided in the blade 8, and a guide portion 81 that engages with and slides in the guide grooves 52 and 62;
82. A rotary compressor characterized by being provided with 82. [Claim 2] Face surface 51 of guide grooves 52 and 62
, 61 is located closer to the center of the bore 41 than the maximum eccentric position of the roller 7, and the guide portion 81,
2. The rotary compressor according to claim 1, wherein the roller 7 wraps around the end surface of the roller 7.