JPS6215506Y2 - - Google Patents

Description

[Detailed Description of the Invention] The present invention relates to a vane type rotary fluid machine used as a pump or a motor.

In conventional vane-type rotary fluid machines, when fluid flows in and out between the inflow and outflow ports and the vane chamber, the shape of the side end corners of the rotor's outer circumferential surface becomes an obstacle to fluid inflow and outflow, and the volume reduce efficiency,
In terms of pump efficiency, it was extremely inefficient.

In other words, in conventional vane-type rotary fluid machines, especially vane-type high-pressure, high-speed rotary fluid machines, the vane chamber, which is surrounded by the vane, the outer peripheral surface of the rotor, the inner peripheral surface of the cam ring, and the side plate, has a relative displacement as the volume inside the vane chamber increases. When fluid flows into the vane chamber, which has a smaller cross-sectional area than the suction port, which has a larger cross-sectional area, the passage area through which the fluid flows rapidly decreases in a stepwise manner, which increases the resistance to flow into the vane chamber. Since the amount of fluid flowing into the chamber is reduced, the volumetric efficiency of the fluid machine is reduced as a result. In addition, contracted flow occurs near the suction port side of the rotor's outer peripheral surface, which equivalently narrows the pipeline by more than the cross-sectional area of the vane chamber, causing the flow to separate from the walls that make up the vane chamber, causing vortices and bubbles. As this occurs, the flow rate of the fluid increases, the pressure inside the vane chamber decreases locally, and when the air separation pressure is reached, dissolved air etc. separates and bubbles (cavitation) occur.
will occur. Moreover, the volume of very small bubbles mixed in the fluid during inflow increases as the pressure decreases, and the amount of fluid flowing into the vane chamber decreases by the amount that these bubbles are generated or increased. Then, the vane chamber is separated from the suction port, and in the process of entering the discharge port, by the time the fluid mixed with bubbles reaches the discharge pressure, the volume of the bubbles decreases as the pressure increases, or the bubbles dissolve in the fluid. As a result, an extra amount of fluid must be returned from the discharge port to fill the volume of the reduced bubbles, which not only causes a decrease in pump efficiency, but also causes instantaneous fluctuations in the amount of fluid delivered at the discharge port. This causes pressure pulsations and causes vibrations, noise, etc. In addition, rapid jet flow also induces fluid sound and causes noise generation.

In order to prevent these problems, conventionally, as shown in FIG. 1, the side end corners 4 of the rotor outer circumferential surface 3 are chamfered over the entire circumferential surface. That is, this is to reduce the rapid decrease in the passage area when fluid flows into the vane chamber from the suction port 1 when the vane chamber 5 is in the suction region. By preventing contraction of the flow, the inflow pressure loss is minimized and cavitation is prevented.

However, in conventional vane-type rotary fluid machines in which the side end corners of the rotor outer peripheral surface are chamfered over the entire circumference, chamfering certainly reduces inflow resistance and prevents cavitation. However, this causes the disadvantages described below.

One of the disadvantages of chamfering the entire circumference is that the area where direct pressure acts on the vane VA increases by the amount corresponding to the chamfering applied to the end corner 4 on the rotor outer circumferential surface. (not shown) becomes longer, the leakage amount of high-pressure fluid increases accordingly, and the volumetric efficiency of the rotary fluid machine decreases.

Another disadvantage of chamfering the entire circumference is that because the chamfering is applied to the entire circumferential surface of the side end corners of the rotor outer circumference, the length of the outermost circumference of the vane groove in the rotor axial direction,
In other words, the outermost support width of the rotor of the vane, which receives pressure from the high-pressure side of the vane to the low-pressure side, is reduced by the amount of the chamfer, and the linear pressure of the rotor support width of the vane, that is, the contact force per unit length, increases, and the suction area In this system, the vane is pressed against the inner circumferential surface of the cam ring by the discharge pressure acting on the bottom of the vane or a similar high pressure, and a contact force is generated between the vane and the inner circumferential surface of the cam ring. Due to the contact force, the back surface of the vane is pressed against the rotor's outermost circumferential support width, making it difficult for the vane to slide, and discontinuously following the inner circumferential surface of the cam ring, which increases pressure fluid leakage and pressure pulsation. This is to induce the generation of foreign noise.

Therefore, the inventors of the present invention conducted systematic experiments and theoretical analyses in order to eliminate the above-mentioned problems without impairing the conventional suction characteristics, and as a result, they came up with the present invention.

The purpose of this invention is to facilitate the flow of fluid between the vane chamber and the inflow and outflow ports, to prevent cavitation, and to reduce the contact force with the outermost part of the vane groove provided on the rotor. Smooth sliding makes it easier to follow the inner circumferential surface of the cam ring, and reduces fluid leakage from the gap between the vane and side plate, improving mechanical efficiency, volumetric efficiency, and reducing pressure pulsation and noise. The objective is to provide a vane-type rotary fluid machine that enables.

In other words, the vane type rotary fluid machine of the present invention is
a housing, a cam ring inserted into the housing and fixed in a position-adjustable manner; a drive shaft rotatably supported by the housing; and a cam ring connected to be driven by the drive shaft and coaxial with the drive shaft. a plurality of vanes slidably inserted into guide grooves provided radially on the outer peripheral wall of the rotor; a vane chamber formed between the rotor, the vanes, and the cam ring; and the housing. In a vane-type rotary fluid machine having an inlet port and an outlet port that communicate with a vane chamber arranged on the inner rotor side, a vane groove is placed at an appropriate distance from the vane groove at the side end corner of the rotor outer circumferential surface and It is characterized by forming a chamfer that becomes deeper toward the side edges in the width direction.

In the vane-type rotary fluid machine with the above configuration, the side end corners of the rotor outer peripheral surface are chamfered at an appropriate distance from the vane groove, so the length of the outermost circumference of the vane groove in the rotor axial direction, that is, the length of the vane. The rotor outermost support width of the vane, which receives pressure from the high-pressure side to the low-pressure side, is not affected by chamfering, and the support width increases compared to the conventional example of chamfering the entire circumference, so the linear pressure of the rotor support width of the vane can be reduced. This reduces sliding resistance in the vane groove, prevents the vane from discontinuously following the inner circumferential surface of the cam ring, reduces pressure pulsations, vibrations, noise, etc., and improves mechanical efficiency and pump efficiency. , motor efficiency etc. can be improved.

In addition, the vane type rotary fluid machine of the present invention does not chamfer the entire circumference of the side end corners of the rotor's outer circumferential surface, but instead chamfers the side end corners of the rotor's outer circumferential surface at an appropriate distance from the vane groove. By chamfering the vane, the chamfered part where the pressure of the fluid in the vane chamber was applied is removed, and the seal length on the vane side wall in the radial direction of the vane is shortened. The amount of fluid leaking to the low-pressure side is reduced, and the volumetric efficiency can be improved, and thus the pump efficiency can be improved.

Furthermore, in the vane-type rotary fluid machine of the present invention, the side end corners of the rotor's outer peripheral surface are chamfered at an appropriate distance from the vane groove, so that the vane receives fluid pressure from the high-pressure side to the low-pressure side of the vane. The area of the rotor is reduced by an appropriate distance from the vane groove compared to the case where the entire circumferential surface of the side end corners of the rotor's outer circumferential surface is chamfered, and this is due to the pressure of the fluid acting on the vane. The acting force is reduced, the sliding resistance of the vane is reduced, and it is possible to prevent the vane from discontinuously following the inner circumferential surface of the cam ring, thereby improving mechanical efficiency and, by extension, pump efficiency.

In addition, the vane type rotary fluid machine of the present invention has chamfers that become deeper as it goes to the side edges of the rotor outer circumferential surface in the width direction to the side end corners of the rotor outer circumferential surface. It maintains the effect of facilitating the flow of fluid into and out of the inlet port and the effect of preventing cavitation.

In carrying out the present invention, the following aspects may be adopted.

A first aspect of the present invention is to form a chamfer at an appropriate distance from the vane groove at the side end corner of the rotor outer peripheral surface that constitutes the low-pressure side vane chamber of the two vane chambers partitioned by the vanes. This is what I did.

In the first aspect, since chamfering is performed at the side end corners of the rotor outer circumferential surface on the low pressure side of the vane at an appropriate distance from the vane groove, the length of the outermost circumference of the vane groove in the rotor axial direction, In other words, the rotor outermost support width of the vane, which receives the pressure of the fluid from the high pressure side to the low pressure side of the vane during the process from suction to discharge, is not affected by chamfering, and the linear pressure of the vane support width is lower than before. Therefore, the sliding resistance of the vane in the vane groove is reduced, preventing the vane from discontinuously following the inner peripheral surface of the cam ring, and preventing fluid leakage.
Pressure pulsations, vibrations, noise, etc. can be reduced, and pump efficiency can be improved.

In addition, in the first aspect, instead of chamfering the entire circumferential surface of the side end corners of the rotor outer circumferential surface, appropriate chamfering is performed from the vane groove to the low pressure side of the vane at the side end corners of the rotor outer circumferential surface. Since the chamfers are applied at intervals, fluid leakage from the chamfered part of the rotor on the high-pressure side of the vane is prevented at the end of the vane groove on the low-pressure side.As a result, the seal length on the vane side wall, that is, the rotor The length in the radial direction of the vane is reduced by the amount of chamfering at appropriate intervals, that is, by the amount of not chamfering, which reduces the amount of fluid leaking from the high-pressure side of the vane to the low-pressure side. Efficiency can be improved.

Furthermore, in the first aspect, the side end corners of the rotor outer circumferential surface are chamfered at an appropriate distance from one side of the vane groove, so the chamfer formation area is restricted to only one side, which facilitates machining. It is.

In addition, in the first aspect, the side end corners of the rotor's outer circumferential surface are chamfered, which facilitates the flow of fluid between the vane chamber and the inflow and outflow ports, and also has the effect of preventing cavitation. , pump efficiency can be improved.

A second aspect of the present invention is that chamfers are formed at appropriate intervals from the vane grooves at the side end corners of the rotor outer peripheral surface constituting two vane chambers partitioned by the vanes. .

In this second aspect, since the side end corners of the rotor outer peripheral surface are chamfered at an appropriate distance from the vane groove, the length of the outermost circumference of the vane groove in the rotor axial direction, that is, from the high pressure side of the vane to the low pressure side. The supporting width of the rotor outermost periphery of the vanes that receive the pressure of the fluid to the side is not affected by the chamfering, and the supporting width is increased compared to the conventional example in which the side end corners of the rotor outer periphery are chamfered over the entire circumference. Therefore, by lowering the linear pressure of the rotor support width of the vane, the sliding resistance of the vane in the rotor guide groove is reduced, and discontinuous tracking of the vane to the inner peripheral surface of the cam ring is prevented, thereby reducing pressure pulsation and vibration.・Noise etc. can be reduced and pump efficiency can be improved.

In addition, in the second aspect, instead of chamfering the entire circumferential surface of the side end corners of the rotor outer circumferential surface, the side end corners of the rotor outer circumferential surface are chamfered at appropriate intervals on both sides of the vane groove. Since the chamfer is applied, the chamfered part where the high pressure of the fluid in the vane chamber was applied is also removed, and the length of the seal in the rotor radial direction on the vane side wall is shortened, so an appropriate adjustment is made only on the low pressure side of the vane. Compared to the first embodiment described above in which chamfers are provided at intervals to indirectly prevent leakage, the amount of fluid leaking from the high-pressure side of the vane to the low-pressure side is further reduced, and the volumetric efficiency is further improved. Pump efficiency can be further improved.

Furthermore, in this second aspect, the side end corners of the rotor outer circumferential surface are chamfered at appropriate intervals from both sides of the vane groove, so that the vane receives the pressure of the fluid from the high pressure side to the low pressure side of the vane. Compared to the case where the entire circumferential surface of the side end corners of the rotor's outer circumferential surface is chamfered, the area is reduced by the appropriate spacing, and the acting force due to the fluid pressure acting on the vane is reduced. , the sliding resistance of the vane is reduced, preventing the vane from discontinuously following the inner circumferential surface of the cam ring, improving mechanical efficiency and, in turn, improving pump efficiency.

In addition, the second aspect makes it easier for fluid to flow in and out between the vane chamber and the inflow and outflow ports by chamfering the side end corners of the outer peripheral surface of the rotor, thereby preventing cavitation. Therefore, pump efficiency can be improved.

In the second aspect, since regions without chamfers are formed on both sides of the vane groove, similar effects can be obtained even when the pump and motor are used in forward and reverse rotation.

Here, when chamfering the side end corners of the rotor outer peripheral surface at an appropriate interval from the vane groove, the numerical range of the "appropriate interval" is preferably 0.1 to 20 mm.
and more preferably 0.5 to 5 mm.
The numerical range of "appropriate spacing" is set to 20 mm or less because if it exceeds 20 mm, the effect of facilitating the flow of fluid between the vane chamber and the inflow/outflow port and the effect of preventing cavitation due to chamfering will be insufficient. This is because they cannot make full use of their abilities.

In addition, the reason why it is set to 0.1 mm or more is because if it is less than 0.1 mm, the thickness in the rotation direction of the rotor outermost support width of the vane, which is not affected by chamfering, becomes thinner due to the "spacing", which reduces sliding resistance. In addition, the length of the seal in the radial direction of the rotor on the side wall of the vane, which has become shorter due to the "spacing", has become narrower, and the effect of reducing the amount of fluid leakage has been reduced. This is because they are unable to perform to their full potential. Furthermore, when the "appropriate interval" is 0.5 mm to 5 mm, the effects of the present invention can be further achieved.

Further, the above-mentioned "appropriate interval" may be a similar "interval" provided at the side end corner of the rotor's outer circumferential surface for each vane, or a different "interval" may be provided, and the above-mentioned range It's fine if it's inside.

In addition, when chamfering the side end corners of the rotor outer circumferential surface at appropriate intervals from both ends of the vane groove, the "appropriate interval" may be a similar "interval" from both ends of the vane groove. , or different "intervals"
may be provided, as long as it is within the above range.

Hereinafter, a vane type rotary fluid machine according to a first embodiment of the first aspect of the present invention will be described with reference to FIGS. 2 to 4.

The vane-type rotary fluid machine of the first embodiment applies the present invention to a constant displacement vane motor, and the rotor has an outer peripheral surface of the rotor constituting the vane chamber on the low pressure side of two vane chambers partitioned by the vanes. It is characterized in that the side end corners are cut linearly at an appropriate distance from the vane groove.

Below, the configuration and effects of the vane type rotary fluid machine of the first embodiment will be explained in detail.

In the vane type rotary fluid machine of the first embodiment, a drive shaft DS is rotatably supported by a flat bearing BR driven into a housing HA. A rotor RT, which is sandwiched between the side plate SP1 and the side plate SP2, is connected to be driven by the drive shaft DS, and rotates together with the drive shaft DS, which is arranged coaxially with the drive shaft DS, and a cam ring CR surrounding the rotor RT. is installed. The cam ring CR, side plate SP1, and side plate SP2 are supported by two common parallel pins PP so as not to rotate relative to the housing HA.

The rotor RT has a vane VA as shown in Figure 3.
A side end corner 14 of the rotor outer circumferential surface 13 that constitutes the low-pressure side vane chamber of the two vane chambers partitioned by
A chamfer was provided by sliding a cylindrical tool with a blade in a straight line on the outer peripheral surface of the milling machine at an appropriate distance from the vane groove 16 to form a flat surface.

A plurality of vanes VA are arranged radially in the vane groove 16 of the rotor RT, and vane push-up springs (not shown) are arranged at the bottoms 17 of these vanes VA, so that the vanes VA always move inside the cam ring CR. The vane tip 18 slides to a position where it contacts the circumferential surface, and the vane tip 18 rotates together with the rotor RT along the inner circumferential surface 20 of the cam ring.

The cam ring inner circumferential surface 20 is formed into an elliptical shape, and the distance from the rotor RT changes as the cam ring rotates.Therefore, the cam ring inner peripheral surface 20 is formed by the two vanes adjacent to the rotor RT, the cam ring CR, and the side plates SP1 and SP2. The volume of the space, that is, the vane chamber, is repeatedly compressed and expanded twice per rotation of the drive shaft DS. Then, the side plate SP1 is located at a position communicating with the vane chamber in the middle of the expansion stroke.
and high pressure ports 11a and 11b on SP2
In addition, a low pressure port 12 is provided on the side plate SP1 at a position communicating with the vane chamber in the middle of the compression stroke, and the vane chamber opens to the high pressure port during the expansion stroke to receive fluid from the high pressure port, and during the compression stroke, the low pressure port opens to the high pressure port. Open to drain the fluid inside the vane chamber.

The side plate SP1 is always connected to the cam ring CR by the spring SR inserted between it and the outer cover OC.
is pressed against the side of the side plate SP1.
The inflow pressure of the high pressure port acts on the side surface of the vane chamber to maintain airtightness of the vane chamber.

The housing HA has an inlet FI and an outlet FO, which are high pressure ports 11a and 11b, respectively.
and is communicated with the low pressure port 12.

As described above, the vane type rotary fluid machine of the first embodiment has a vane groove 16 in the side end corner of the rotor outer peripheral surface that constitutes the low pressure side vane chamber of the two vane chambers partitioned into the vane VA. Since the chamfering is performed at appropriate intervals from the vane groove 16, the support width of the rotor outermost periphery of the vane groove 16 is not affected by the chamfering, the sliding resistance of the vane in the vane groove 16 is reduced, and motor efficiency can be improved.

In addition, in the vane-type rotary fluid machine of the first embodiment, instead of chamfering the entire circumferential surface of the side end corner portion 14 of the rotor outer circumferential surface, two
Since the side end corners of the rotor outer circumferential surface constituting the low-pressure side vane chamber of the two vane chambers are chamfered at an appropriate distance from the vane groove 16, the chamfered portion of the rotor RT on the high-pressure side of the vane VA is chamfered. Since fluid leakage is prevented at the end of the vane groove on the low-pressure side, the seal length on the vane side wall, that is, the length in the radial direction of the rotor RT, is equal to the chamfered length at appropriate intervals, that is, The amount of fluid leaked from the high pressure side to the low pressure side of the vane VA can be reduced and the motor efficiency can be improved.

Furthermore, the vane type rotary fluid machine of the first embodiment has a rotor outer circumferential surface 13 constituting the vane chamber on the low pressure side of the two vane chambers partitioned by the vane VA.
Since a chamfer is formed on the side end corner 14 at an appropriate distance from the vane VA, when fluid flows into the vane chamber from the high-pressure ports 11a and 11b, there is resistance to the fluid flowing into the front side of the vane VA. This makes it possible to reduce the increase in hydraulic pressure acting on the front side of the vane VA and improve motor efficiency.

Further, the chamfering of the end corner 14 of the outer peripheral surface of the rotor is formed by linear cutting in one stroke, so that machining is easy.

Hereinafter, a vane type rotary fluid machine according to a second embodiment of the first aspect of the present invention will be explained with reference to FIGS. 5 to 7.

The vane type rotary fluid machine of the second embodiment applies the present invention to a variable displacement vane pump, and the side end angle of the outer circumferential surface of the rotor constituting the vane chamber on the low pressure side of two vane chambers partitioned by vanes. The vane groove is chamfered at an appropriate distance from the vane groove so that the amount of chamfering is uniform in the circumferential direction, and the end portion is chamfered with an arc of a certain curvature when viewed in longitudinal section. That is.

Below, the configuration and effects of the vane type rotary fluid machine of the second embodiment will be explained in detail, focusing on the differences from the first embodiment.

In the vane type rotary fluid machine of the second embodiment, the drive shaft DS is rotatably supported by a bearing (not shown) driven into the housing HA. Next, a rotor RT connected to be driven by the drive shaft DS, disposed coaxially with the drive shaft DS, and rotating integrally with the drive shaft DS, and a perfectly circular cam ring CR surrounding the rotor RT are disposed. The position of the cam ring CR can be changed by adjusting the spring 81 via the push rod PR. Further, the thrust block TB is provided to prevent the cam ring CR from moving in the vertical direction and to smoothen its movement from side to side.

A plurality of vanes VA are arranged radially in the vane groove 26 of the rotor RT, and these vanes VA are
Due to the rotational centrifugal force acting on the vane VA and the hydraulic pressure acting on the vane bottom 27 due to the pump discharge pressure guided to the oil sump groove 29, the vane tip 28 slides to a position touching the inner circumferential surface of the cam ring CR, and the vane tip 28 is moved to the inner circumference of the cam ring. It rotates along the plane 30 together with the rotor RT.

The rotor RT is arranged at an appropriate distance from the vane VA at the side end corner 24 of the rotor outer peripheral surface 23 that constitutes the low-pressure side vane chamber of the two vane chambers partitioned by the vane VA, as shown in FIG. A chamfer is formed so that the amount of chamfering is uniform in the circumferential direction, and the end is formed by an arc of a certain curvature when viewed along the circumference and in a longitudinal section. The chamfer is
This was done by applying the end mill tool of a milling machine to the chamfered portion of the end corner of the outer peripheral surface of the rotor and moving it in a straight line so that the end surface formed a curvature.

The cam ring inner circumferential surface 30 is composed of a circumferential surface having an inner diameter larger than the outer circumferential surface of the rotor RT, and by moving its axis position relative to that of the rotor RT, the distance from the rotor RT changes as the cam ring rotates. As a result, the volume of the space formed by the rotor RT, the two adjacent vanes, the cam ring CR, and the side plate (not shown), that is, the vane chamber 25, is compressed once per rotation of the drive shaft DS. It seems to be expanding repeatedly. A suction port is provided in the side plate at a position communicating with the vane chamber in the middle of the expansion stroke, and a discharge port is provided in the side plate at a position communicating with the vane chamber in the middle of the compression stroke. It opens to the suction port to suck in fluid from the suction port, and in the compression stroke, opens to the discharge port to discharge the fluid in the vane chamber.

As described above, the vane type rotary fluid machine of the second embodiment not only achieves the effects of the first aspect described above, but also has a surface on the side end corner 24 of the rotor outer peripheral surface 23 in the circumferential direction. Since the chamfer is applied so that the intake amount is uniform, the inflow area of the fluid between the suction port and the vane chamber 25 does not change even when the rotor RT rotates, and the inflow amount remains constant, improving pump efficiency. can be improved.

In addition, the chamfering at the side end corners 24 of the rotor outer circumferential surface 23 is shaped so that the end is an arc of a certain curvature when viewed in longitudinal section, so that the inflow port, outflow port, and vane chamber are The flow of fluid between the pumps becomes smooth and easy, the contraction of flow is alleviated, and the volumetric efficiency can be improved. Also, the effect of preventing cavitation can be achieved, and the pump efficiency can be improved.

Hereinafter, a vane type rotary fluid machine according to a third embodiment of the second aspect of the present invention will be described with reference to FIGS. 8 and 9.

The vane-type rotary fluid machine of the third embodiment applies the present invention to a constant-displacement vane pump, and has vane grooves adjacent to each other at the side end corners of the outer circumferential surface of the rotor, which constitute two vane chambers partitioned by vanes. The feature is that the center portion is cut circularly and chamfered at appropriate intervals.

Below, the configuration and effects of the vane type rotary fluid machine of the third embodiment will be explained in detail, focusing on the differences from the above-mentioned embodiments.

In the vane type rotary fluid machine of the third embodiment, eight vane grooves 36 for sliding the vanes are arranged radially on the outer peripheral wall of the rotor RT.

As shown in FIGS. 8 and 9, the rotor RT has a central portion located at an appropriate interval on both sides from the vane groove 36 of the side end corner 34 of the rotor outer circumferential surface 33.
A tool with a blade formed on the cylindrical surface of a milling machine is pressed against the cylindrical surface of the milling machine to cut it into a circular arc shape, and when viewed from a longitudinal section, the cutting edge forms a straight chamfer.

As described above, in the vane-type rotary fluid machine of the third embodiment, the side end corners 34 of the rotor outer peripheral surface 33 are chamfered at appropriate intervals on both sides of the vane, so that the vane grooves 36 are chamfered. The length of the outermost circumference in the axial direction of the rotor, that is, the support width of the vane that receives the pressure of the fluid from the high pressure side to the low pressure side of the vane, is not affected by the chamfering, and the chamfering is applied to the entire outermost circumferential surface of the rotor outer circumferential surface. Since the support width is increased compared to the conventional example, the linear pressure of the rotor support width of the vane VA is lowered, the sliding resistance of the vane VA in the vane groove 36 of the rotor RT is reduced, and the inner circumference of the cam ring of the vane VA is reduced. It is possible to prevent discontinuous tracking to the surface, reduce pressure pulsations, vibrations, noise, etc., and improve pump efficiency.

In addition, since the side end corners 34 of the rotor outer peripheral surface 33 are chamfered at appropriate intervals on both sides of the vane groove 36, the length of the seal on the side wall of the vane VA, that is, the length in the rotor radial direction, can be adjusted appropriately. The amount of fluid leaking from the high-pressure side of the vane VA to the low-pressure side is reduced by the amount of chamfering at intervals of can be reduced and pump efficiency improved.

Furthermore, since the side end corners 34 of the rotor outer peripheral surface 33 are chamfered at appropriate intervals on both sides of the vane groove 36, the area of the vane VA that receives the pressure of the fluid from the high pressure side to the low pressure side of the vane VA is reduced. Compared to the case where the entire circumferential surface of the side end corner 34 of the rotor outer circumferential surface 33 is chamfered, it is reduced by an appropriate distance on the high pressure side of the vane VA, and the sliding resistance of the vane VA is reduced. This can prevent the vane VA from discontinuously following the inner peripheral surface of the cam ring, and can improve pump efficiency.

In addition, since the side end corners 34 of the rotor outer circumferential surface 33 are chamfered, fluid can easily flow in and out between the suction port, the discharge port, and the vane chamber, improving volumetric efficiency, and preventing cavitation. It is also effective, and pump efficiency can be improved.

In addition, in this second aspect, since regions where chamfering is desired are formed on both sides of the vane groove, the pump can be
Even if the rotation is reversed, the same effect can be obtained.

Further, the chamfering of the side end corners 34 of the rotor outer circumferential surface 33 is performed by pressing a tool with a blade formed on the cylindrical surface of a milling machine at appropriate intervals on both sides of the vane VA, making the chamfering work easy. It is.

A vane type rotary fluid machine according to a fourth embodiment of the second aspect of the present invention will be described below with reference to FIGS. 10 to 12.

The vane type rotary fluid machine of the fourth embodiment applies the present invention to a variable displacement vane motor, and has adjacent vane grooves at the side end corners of the rotor outer peripheral surface that constitute two vane chambers partitioned by the vanes. It is characterized by forming chamfers by linearly cutting the central portion at appropriate intervals.

The configuration and effects of the vane-type rotary fluid machine according to the fourth embodiment will be explained below, focusing on the differences from the above-mentioned embodiments.

In the vane type rotary fluid machine of the fourth embodiment, a drive shaft DS is rotatably supported by a ball bearing BR driven into a housing HA. The rotor RT is sandwiched between the side plate SP and the cover plate CP, is connected to be driven by the drive shaft DS, and rotates together with the drive shaft DS, which is arranged coaxially with the drive shaft DS, and the cam ring surrounding it. CR is provided. The cam ring CR is pushed upward by the hydraulic pressure acting on the inner circumferential surface 50 and is pressed against the end surface 83 of the adjusting screw 82.
A spring force (not shown) acts on the left side, and a piston (not shown) that controls the position of the cam ring and the rotation speed of the rotor RT and drive shaft DS is in contact with the right side. There is.

Four vanes VA are arranged radially in the vane groove 46 of the rotor RT, and the bottom 4 of these vanes
A guide ring (not shown) is disposed at 7, and the vane VA always slides to a position where it touches the inner circumferential surface 50 of the cam ring CA, and the vane tip 48 rotates along the inner circumferential surface 50 of the cam ring together with the rotor RT. do.

When the rotor RT is viewed in longitudinal section as shown in FIG. 12 with an appropriate distance from the vane groove 46 at the side end corner 44 of the rotor outer circumferential surface 43 that constitutes two vane chambers partitioned by the vane VA. A cylindrical tool with a cutting edge on the outer circumferential surface is slid in a curved shape using a milling machine to form a flat surface in the middle part between the vanes VA so that the end part is composed of an arc with a certain curvature. I cut and chamfered it.

The cam ring inner circumferential surface 50 is formed so that the distance from the rotor RT changes as it rotates.
The volume of the space formed by the CP, that is, the vane chamber, is expanded and compressed repeatedly once per rotation of the drive shaft DS.

Hereinafter, the hydraulic circuit of this embodiment will be explained based on FIG. 10.

Side plate SP and cover plate CP have A ports AP1 and AP2 and B port BP1.
and BP2 are provided. Hydraulic supply device 8
Pressure oil from 4 is connected to P line by solenoid valve 85.
When PL and X line XL are connected, pressure oil passes through X line XL and flows from inlet port FB1 to A port AP1.
and is supplied to AP2. During the expansion stroke, the vane chamber opens to A ports AP1 and AP2, which are high-pressure ports by communicating P line PL and X line XL, and supplies fluid to A port.
The rotor RT rotates due to the fluid force received from AP1 and AP2 and acts on the back surface of the vane, and during the compression stroke, the B port serves as a low pressure port.
Opens in BP1 and BP2 to let out the low pressure fluid in the vane chamber. Thereby, rotor RT and drive shaft
DS is rotated in the M direction.

On the other hand, when the P line PL and the Y line YL are communicated by the solenoid valve 85, the pressure oil flows through the outflow port FB2.
The oil is supplied to the B ports BP1 and BP2 to rotate the rotor RT and the drive shaft DS in the N direction, and returns to the oil tank 86 from the A ports AP1 and AP2, which are low pressure ports, through the inlet and outlet FB1.

As described above, the vane type rotary fluid machine of the fourth embodiment not only achieves the effects of the second aspect described above and improves motor efficiency, but also has the following effects.

In the vane-type rotary fluid machine of the fourth embodiment, since both sides of the side corner portions 44 of the rotor outer circumferential surface 43 are chamfered linearly, the communication area between the port and the vane chamber sharply increases as the rotor rotates. A because it does not change to
Fluctuations in fluid flow between the port and the B port and the vane chamber are smoothed, and motor efficiency can be improved.

Further, the chamfering of the side end corners 44 of the rotor outer circumferential surface 43 can be done in one stroke with a milling machine as described above, so that the chamfering work is easy.

Furthermore, although the vane type rotary fluid machine of this embodiment is a vane motor that can control the rotation direction, since the vane grooves 46 are chamfered at appropriate intervals on both sides, even if the rotation direction changes, the above-mentioned effect can be maintained. The effects of the second aspect can be achieved similarly.

Hereinafter, a vane-type rotary fluid machine according to a fifth embodiment of the second aspect of the present invention will be illustrated in FIGS. 13 to 15.
This will be explained using figures.

The vane-type rotary fluid machine of the fifth embodiment applies the present invention to a constant displacement vane pump, and provides suitable airflow from the vanes to the side end corners of the outer circumferential surface of the rotor, which constitute two vane chambers partitioned by the vanes. The chamfer is characterized in that the amount of chamfering is uniform in the circumferential direction at intervals, and the chamfering is formed by an arc of curvature at the end when viewed in longitudinal section.

Below, the configuration and effects of the vane type rotary fluid machine of the fifth embodiment will be explained in detail, focusing on the differences from the above-mentioned embodiments.

In the vane type rotary fluid machine of the fifth embodiment, first, the housing HA is made of a hollow cylindrical member, and the housing HA has a large diameter portion HA1 and a small diameter portion HA2. The small diameter part HA2 of the housing HA is a plain bearing BR.
and a drive shaft DS, which can be rotated by a flat bearing BR driven into the housing HA.
is pivoted. Large diameter part HA of housing HA
1 is rotor RT, vane VA, cam ring CR,
Side plates SP1 and SP2, parallel pin PP,
Includes spring SR and outer cover OC.

A rotor RT is sandwiched between side plates SP1 and SP2, spline-coupled to be driven by the drive shaft DS, arranged coaxially with the drive shaft DS, and rotates together with the drive shaft DS, and a reciprocating vane around the rotor RT. Cam ring CR as a guide wheel that regulates movement
and are provided. The cam ring CR and the side plates SP1 and SP2 are assembled in a non-rotatable manner relative to the housing HA by two common parallel pins PP.

Eight vanes VA are arranged radially in the vane groove 56 of the rotor RT, and these vanes VA are caused by the rotational centrifugal force acting on the vanes VA and the pump discharge pressure led to the oil sump groove 59 to cause the vane bottom 57 to The applied hydraulic pressure causes the vane tip 58 to slide to a position where it contacts the inner circumferential surface 60 of the cam ring CR, and the vane tip 58 rotates along the cam ring inner circumferential surface 60 together with the rotor RT.

The rotor RT is circumferentially spaced from a vane groove 56 by 1 mm on the low pressure side and 2 mm on the high pressure side at a side end corner 54 of the rotor outer peripheral surface 53 that constitutes two vane chambers partitioned by the vane VA. Chamfer amount H=
A chamfer is formed so that it is uniform at 5 mm, and the end is an arc of a certain curvature when viewed in a longitudinal section, and the chamfer is
The end mill tool of the milling machine is attached to the rotor outer peripheral surface 53.
This was done by applying the cut to the chamfered portion of the side end corner 54 of the cutter and cutting it in a straight line while moving it so that the end face formed a curvature.

The cam ring inner circumferential surface 60 is formed so that the distance from the rotor RT changes as it rotates, and thereby the space formed by the rotor RT and the two adjacent vanes, the cam ring CR, and the side plates SP1 and SP2, that is, the vane. Shaft driving chamber volume
Compression and expansion are repeated twice per rotation of the DS. Then, the suction ports 51a and 51b of the side plates SP1 and SP2, which are in communication with the vane chamber in the middle of the expansion stroke, are
In addition, a discharge port 52 is provided on the side plate SP1 at a position communicating with the vane chamber in the middle of the compression stroke.
During the expansion stroke, the vane chamber opens to the suction port to suck in fluid from the suction port, and during the compression stroke, the vane chamber opens to the discharge port to discharge the fluid in the vane chamber.

The side plate SP1 is always connected to the cam ring CR by the spring SP inserted between the outer cover OC.
is pressed against the side of the side plate SP1.
Discharge pressure acts on the side surfaces of the vane chamber to maintain airtightness of the vane chamber.

The housing HA has a suction port FI and a discharge port FO, which are suction ports 51a and 51b, respectively.
and is communicated with the discharge port 52.

As described above, in the vane type rotary fluid machine of the fifth embodiment, the side end corners 54 of the rotor outer peripheral surface 53 are chamfered at appropriate intervals on both sides of the vane VA, so that the rotor RT The axial length of the outermost circumference of the vane groove 56, that is, the support width of the vane VA that receives pressure from the high-pressure side to the low-pressure side of the vane, is not affected by the chamfer, compared to the conventional example in which the entire circumferential surface is chamfered. Since the support width increases, the vane groove 56
The sliding resistance of the vane VA is reduced, and the vane
By preventing VA from discontinuously following the cam ring inner peripheral surface 60, it is possible to reduce fluid leakage, pressure pulsation, vibration, noise, etc., and improve mechanical efficiency, which in turn improves pump efficiency. .

In addition, the vane type rotary fluid machine of the fifth embodiment has vanes at the side end corners 54 of the rotor outer circumferential surface 53.
Since the chamfers are placed at appropriate intervals from both sides of the VA, the length of the seal on the side wall of the vane VA, that is, the length in the radial direction of the rotor RT, is reduced by the chamfers at appropriate intervals. , Vane VA
Compared to the case where chamfers are provided at appropriate intervals on only one side of the vane, the amount of fluid leaking from the high-pressure side to the low-pressure side of the vane VA is further reduced, which further improves volumetric efficiency, which in turn increases pump efficiency. It can be further improved.

Furthermore, the vane type rotary fluid machine of the fifth embodiment has vanes at the side end corners 54 of the rotor outer circumferential surface 53.
Since chamfering is performed at appropriate intervals on both sides of the vane VA, the area of the vane VA that receives fluid pressure from the high pressure side to the low pressure side of the vane VA is reduced to the rotor outer peripheral surface 53.
Compared to the case where the entire circumferential surface of the side end corner portion 54 is chamfered, only a portion placed at an appropriate interval on the high pressure side of the vane VA is reduced, the sliding resistance of the vane VA is reduced, and the vane VA can be prevented from discontinuously following the cam ring inner circumferential surface 60, improving mechanical efficiency and, by extension, pump efficiency.

In addition, in the vane type rotary fluid machine of the fifth embodiment, the side end corners 54 of the rotor outer circumferential surface 53 are chamfered so that the amount of chamfering is uniform in the circumferential direction. Even if the rotor RT rotates within this region, the inflow area of the fluid between the suction ports 51a and 51b and the vane chamber does not change, and the inflow amount remains constant, making it possible to improve pump efficiency.

Further, since the chamfering at the side end corners 54 of the rotor outer circumferential surface 53 is shaped so that the end is constituted by an arc of a certain curvature when viewed in a longitudinal section, the suction ports 51a, 51b and the discharge port 52 The inflow and outflow of fluid between the vane chamber and the vane chamber becomes smooth, flow separation and contraction are alleviated, and volumetric efficiency can be improved.It also has the effect of preventing cavitation, and improves pump efficiency. can.

Hereinafter, the vane type rotary fluid machine of the sixth embodiment belonging to the second aspect of the present invention will be explained as shown in FIGS. 16 to 18.
This will be explained using figures.

The vane type rotary fluid machine of the sixth embodiment applies the present invention to a constant displacement vane pump, the suction port is shaped to communicate with one side of the rotor side of the vane chamber, and the rotor is divided into two parts partitioned by vanes. The chamfer is placed at an appropriate distance from the vane groove on the side where the suction port is located at the side end corner of the rotor outer circumferential surface constituting the two vane chambers, so that the amount of chamfering is uniform in the circumferential direction and in the longitudinal direction. When viewed from the surface, the end face is chamfered in a shape that smoothly connects ``a circular arc of a certain curvature, a straight line, and a circular arc of a certain curvature.''

Below, the configuration and effects of the vane type rotary fluid machine of the sixth embodiment will be explained in detail.

The vane type rotary fluid machine of the sixth embodiment has the same configuration as the fixed displacement vane pump of the fifth embodiment, so the explanation of the parts having the same configuration will be omitted, and the different parts will be described in detail. That's it.

The vane type rotary fluid machine of the sixth embodiment is the 16th embodiment.
As shown in the figure, the air holes 87 are provided at symmetrical positions that communicate with the vane chamber in the middle of the expansion stroke, so that there is no difference in the pressure applied to the side plate SP1 side and the side plate SP2 side that have the suction port 61. It was configured like this.

The housing HA has a suction port (not shown) and a discharge port FO, which communicate with the suction port 61 and the discharge port (not shown), respectively.

The rotor RT has two
As shown in FIG. 18, on the side where the suction ports 61 are arranged at the side end corners of the rotor outer circumferential surface 63 constituting the two vane chambers, Program in advance so that the amount of chamfering is uniform and the end face is chamfered in a shape that smoothly connects "arc of a certain curvature - straight line - arc of a certain curvature" when looking at the longitudinal section. did
The end mill tool of the NC-controlled milling machine was operated based on signals to form a chamfer in the shape shown above.

As described above, the vane type rotary fluid machine of the sixth embodiment has the following effects in addition to the effects of the second aspect described above.

In the vane type rotary fluid machine of the sixth embodiment, the side end corners of the rotor outer peripheral surface 63 are chamfered so that the amount of chamfering is uniform in the circumferential direction.
Even if the RT rotates, the inflow area of the fluid between the suction port 61 and the vane chamber does not change, and the inflow amount remains constant, thereby improving pump efficiency.

Furthermore, in the sixth embodiment, the chamfering at the side end corners of the rotor outer circumferential surface 63 is made so that the end face has a shape that connects a circular arc, a straight line, and a circular arc when viewed in a longitudinal section.
Fluid flows in and out between the suction port 61 and the discharge port and the vane chamber more smoothly and easily, which alleviates flow separation and contraction, improves volumetric efficiency, and also prevents cavitation. , pump efficiency can be improved.

Hereinafter, a vane type rotary fluid machine according to a seventh embodiment of the second aspect of the present invention will be shown in FIGS. 19 and 20.
This will be explained using figures.

The vane-type rotary fluid machine of the seventh embodiment applies the present invention to a constant displacement vane pump, and the vane groove is installed at the side end corner of the outer peripheral surface of the rotor, which constitutes two vane chambers partitioned by the vanes. Chamfers are formed at intervals so that the amount of chamfering is uniform in the circumferential direction, and the amount of chamfering is gradually decreased from the point where the appropriate interval is placed until reaching the vane groove. It is characterized by being chamfered so as to be in contact with the outer circumference of the rotor.

Below, the configuration and effects of the vane type rotary fluid machine of the seventh embodiment will be explained in detail, focusing on the differences from the fifth embodiment described above.

The vane type rotary fluid machine of the seventh embodiment has a rotor
As shown in FIGS. 19 and 20, RT is
The chamfer of the rotor RT is formed so that the amount of chamfering is uniform in the circumferential direction up to a point at an appropriate distance from the vane groove 76 at the side end corner of the rotor outer peripheral surface 73, and from there. The amount of chamfering is gradually reduced until reaching the vane groove 76, and the chamfering is formed so as to be in contact with the outer circumference of the rotor until reaching the vane groove. Further, when looking at the longitudinal section of the rotor, the chamfered end face is formed into an S-shape or an inverted S-shape with a certain curvature. In this example, since the chamfer has a complex shape as described above, a sintering mold corresponding to the chamfer was created in advance, raw material powder was poured into it, and the chamfer was sintered to form the chamfer integrally with the rotor.

As described above, the vane type rotary fluid machine of the seventh embodiment has the following effects in addition to the effects of the second aspect described above.

In the vane type rotary fluid machine of the seventh embodiment, the side end corners of the rotor outer peripheral surface 73 are chamfered so that the amount of chamfering is uniform in the circumferential direction.
Even when RT rotates, the fluid inflow area between the suction port (not shown) and the vane chamber does not change.
The inflow amount becomes constant and pump efficiency can be improved.

Furthermore, the chamfering width at the side end corners of the rotor outer peripheral surface 73 is gradually reduced in the radial direction of the rotor until an appropriate distance is left from the vane groove 76, as shown in FIG. Therefore, the communication area does not change suddenly in accordance with the rotational movement of the rotor, so fluctuations in the inflow amount are further reduced, and pump efficiency can be improved.

Furthermore, the chamfering at the side end corners of the rotor outer circumferential surface 73 is chamfered into an S-shape whose end has a certain curvature when viewed in longitudinal section, so that the suction port, discharge port, and vane The fluid flow between the pump and the chamber is made smoother, further reducing flow separation and contraction, improving volumetric efficiency, and also prevents cavitation, improving pump efficiency. can be done.

In addition, in the first aspect of the present invention, explanation has been given of chamfering when an appropriate interval is placed at the end of the rotor side wall constituting the vane chamber on the low pressure side of the two vane chambers partitioned by the vanes. Even when an appropriate interval is provided on the side, it is possible to reduce the amount of fluid leaking from the high-pressure side of the vane to the low-pressure side of the vane side wall.

In addition, in vane motors, by chamfering the side end corners of the rotor outer circumferential surface that constitutes the high-pressure side vane chamber at appropriate intervals, the gap between the vane tip and the cam ring inner circumferential surface during the expansion stroke and compression stroke is improved. It is possible to increase the support width of the rotor outermost periphery of the vane that receives the frictional force acting on the rotor, reduce the linear pressure of the rotor support width, and improve motor efficiency.

In addition, in a variable displacement vane pump, if the amount of eccentricity is small, the amount of protrusion from the rotor increases in the process of the vane transitioning from the discharge area to the suction area, and in that process, fluid pressure is applied to the back of the vane. Therefore, by chamfering the side edges of the outer peripheral surface of the rotor that constitute the vane chamber on the high-pressure side at appropriate intervals, the area of the vanes that receive this pressure can be reduced, and the area affected by the fluid pressure acting on the vanes can be reduced accordingly. Acting force can be reduced and pump efficiency can be improved.

As described above, the above-mentioned effects can be achieved even when an appropriate distance is provided from the high-pressure side of the vane groove to the side end corner of the outer peripheral surface of the rotor that constitutes the vane chamber on the high-pressure side. Applicable.

[Brief explanation of the drawing]

Figure 1 is a side view of the rotor and cam ring of a conventional vane-type rotary fluid machine, and Figures 2 to 4 are
The figures show a machine according to the first embodiment of the present invention, in which Fig. 2 is a vertical sectional view, Fig. 3 is a side view of the rotor, and Fig. 4 is a side view of the rotor.
The figure is a longitudinal cross-sectional view of the rotor taken along line - in Figure 3;
5 to 7 are views showing a second embodiment of the machine of the present invention, in which FIG. 5 is a cross-sectional view thereof, FIG. 6 is a side view of the rotor, and FIG. 7 is a view of the rotor in FIG. 6. 8 and 9 are views showing a third embodiment of the machine of the present invention, FIG. 8 is a perspective view of the rotor, FIG. 9 is a longitudinal end view of the rotor, and FIG. 12 to 12 show a machine according to a fourth embodiment of the present invention, FIG. 10 is a vertical sectional view and a hydraulic circuit diagram thereof, FIG. 11 is a side view of the rotor, and FIG. 12 is a diagram of the rotor. Longitudinal cross-sectional view along line XII-XII, No. 13
15 to 15 show a machine according to a fifth embodiment of the present invention, in which FIG. 13 is a longitudinal sectional view thereof, FIG. 14 is a side view of the rotor and cam ring, and FIG. 15 is a longitudinal end view of the rotor. 16 to 18 are views showing a machine according to a sixth embodiment of the present invention, in which FIG. 16 is a partial vertical sectional view, FIG. 17 is a side view of the rotor, and FIG. 18 is a side view of the rotor.
The figures are partial vertical sectional views of the rotor, Figures 19 and 2.
Figure 0 shows the seventh embodiment of the present invention.
FIG. 9 is a side view of the rotor, and FIG. 20 is a partial vertical sectional view of the rotor. In the figure, HA is the housing, DS is the drive shaft, RT is the rotor, VA is the vane, CR is the cam ring, SP is the side plate, CP is the cover plate, SR is the spring, PP is the parallel pin, OC is the outer cover, 3, 13,
23, 33, 43, 53, 63, 73 are the outer peripheral surface of the rotor, 4, 14, 24, 34, 44, 54 are the side end corners of the outer peripheral surface of the rotor, 5, 25, 55 are the vane chambers, 16, 26 , 36, 46, 56, 66, 76
is the vane groove, 17, 27, 47, 57 is the vane bottom, 18, 28, 48, 58 is the vane tip, 2
Reference numerals 9 and 59 indicate oil reservoir grooves, and 20, 30, 50, and 60 indicate inner circumferential surfaces of the cam rings, respectively.

Claims (1)

[Claims for Utility Model Registration] (1) A housing, a cam ring inserted into the housing and fixed in a position-adjustable manner, a drive shaft rotatably supported by the housing, and a drive shaft driven by the drive shaft. A rotor that is connected to the drive shaft and arranged coaxially with the drive shaft, a plurality of vanes that are slidably inserted into vane grooves provided radially on the outer peripheral wall of the rotor, and a rotor, vanes, and cam ring. In a vane-type rotary fluid machine having a vane chamber formed between the housing and an inflow port and an outflow port communicating with the vane chamber arranged on the rotor side in the housing, a vane groove is formed at a side end corner of the rotor outer circumferential surface. A vane-type rotary fluid machine, characterized in that chamfers are formed at appropriate intervals and become deeper toward the side edges in the width direction of the outer circumferential surface of the rotor. (2) A utility model characterized in that a chamfer is formed at an appropriate distance from the vane groove at the side end corner of the outer peripheral surface of the rotor that constitutes the vane chamber on the low-pressure side of the two vane chambers divided by the vanes. A vane-type rotary fluid machine according to registered claim (1). (3) Utility model registration claim No. 1, characterized in that chamfers are formed at appropriate intervals from the vane grooves at the side end corners of the outer peripheral surface of the rotor constituting the two vane chambers partitioned by the vanes. (1)
The vane type rotary fluid machine described in .