JPS60256582A - Vane pump - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a vane pump comprising a pair of hook-shaped square vanes slidably arranged next to each other in a guiding slit of a rotor. The hook head of the vane and both stems of both vanes located in line with each other (1) have a thickness that matches the slink width of the 5 guide slits, and each stem foot of one vane and each stem foot of the other vane are A hook chamber is formed between the vane and the hook head of the rotor, and the hook chamber is recessed into the guide slit of the rotor over a partial rotation range of the rotor.

BACKGROUND OF THE INVENTION A vane pump of this type is known, for example, from Japanese Utility Model Publication No. 6486/1986.

Problems to be solved by the present invention This type of vane is similar to general vane pumps.

In pumps as well, the vanes are in close contact with the inner circumferential surface of the casing at any rotational position of the rotor, which creates the problem that the vanes must constantly and repeatedly retract and protrude in the radial direction. In known vane pumps, the total length of the vane is equal to the casing radius, and therefore the maximum rotor rotational position (maximum rotor position)
, in other words, at the position (bottom dead center) where the vane is completely recessed into the slit of the rotor, K-.

Because the distance between the center of gravity of the vane and the center of the rotor is extremely small, or because the center of gravity of the vane is located on the opposite side of the two axes, sufficient centrifugal force acts on the vane within the rotation range of the rotor. Therefore, the vane head is not kept in contact with the casing peripheral wall.

In known vane pumps, therefore, both parts are supported relative to each other by springs. However, the disadvantage of doing so is that the spring force is at a minimum at the rotor position (maximum rotor position) where the spring force is absolutely necessary for the vane to emerge from bottom dead center. On the other hand, the rotor is set at an angle of 90 degrees with respect to the maximum position of the rotor where the total vane length is minimum.
At the zero rotation position (minimum rotor position), the spring force is at its maximum and the center of gravity of the vane is on the protruding side with the rotation axis as the boundary. Therefore, the centrifugal force acting on the vane head is unnecessarily supported by the maximum spring force after the minimum position □ of the rotor.

The resulting increased friction increases power losses.

Therefore, an object of the present invention is to apply an additional force to the vane to support the protrusion movement of the vane only while the centrifugal force is insufficient to cause the protrusion movement of the vane. .

Means of the Invention that Solved the Problems The structure of the present invention that solved the above problems is such that the retraction of the hook chambers is performed within a rotational range between the front angle of the bottom row point 900 and the bottom dead center ridge angle of 9000, and that each hook chamber is is filled with oil during the partial rotation from the bottom dead center forward angle 900 to the bottom dead center, and is released via the throttle during the partial rotation from the bottom dead center to the bottom dead center exit angle 90Q.

Effect of the present invention According to the configuration of the present invention, the hook chamber (in short, the cubic space between the hook head of one vane and the stem foot of the other vane) is located at the minimum position of the rotor (at the front corner 900 of the lower row point). position) into the rotor's ° guide slit. This closes the hook chamber airtight on all sides. Furthermore, according to the invention, the flap chamber is filled with oil between the position of the front corner 900 of the lower row point and the bottom dead center.

This is effectively done because the hook chamber increases in volume in this range of rotation, since the overall length of the vane increases. Therefore, even if there is a leak, sufficient lubricating oil is sucked into the seven chambers. The hook room is 1
At points or over a part of the rotational range, or over the entire rotational range between the position of the lower row point front corner 900 and the bottom dead center, it is connected to an oil source, preferably a lubricating oil source. Further, according to the present invention, the hook chamber is restricted to the inside of the pump or to the outside, especially to the lubricating oil tank, within the rotation range between the bottom dead center and the next minimum position after the bottom dead center (90 degrees of bottom dead center clearance angle). connected via

In that case, due to the volume reduction in the hook chamber 9 within the rotational range between bottom dead center and the minimum position after bottom dead center, sufficient pressure is created in the hook chamber, which causes the vane to protrude and press against the casing wall. The diaphragm is designed so that

Hook chamber guides at minimum position before bottom dead center, 17
Similarly to the plunge into the slot, the hook chamber again protrudes from the guide slot in the smallest position after bottom dead center, so that at the latest in this minimum position, the additional pressure load on the protruding bar disappears. do.

According to the invention, an outlet with a variable throttle is further provided over the rotational range between the bottom dead center and the bottom dead center ridge angle 900 position. This variable throttle can be designed in particular in such a way that the pressure in the hook chamber dissipates rapidly before reaching the minimum position after bottom dead center. For this purpose, it is also possible to provide an additional outlet, for example in the form of a radially restricted notch on the front side of the hook head, thereby allowing an early connection of the hook chamber to the casing end wall.

The oil supply to the hook chamber as well as the throttling oil discharge from the hook chamber can take place, for example, by a groove in the end wall of the casing, the cross-section of which can then be adapted to the desired throttling action. This groove preferably extends over a partial circle traced by the hook chamber between the minimum position before the bottom dead center and the minimum position after the bottom dead center.

Furthermore, oil supply and squeezable oil drainage can also be effected by providing cutouts in the end wall of the rotor.

The outer diameter of this notch is dimensioned such that the notch is traced by the hook chamber between the 900 position and the bottom dead center. This connects the hook chamber to the oil supply.

After passing the bottom dead center, the oil in the hook chamber is forced out of the hook chamber through this notch. The limited depth of the cutout produces the desired throttling effect. Advantageously, the recesses vary in depth in the radial direction.

In this case, it is preferable to maximize the depth in the outer region of the notch, so that just before the minimum position after the bottom dead center, the oil is hardly squeezed out and is discharged from the hook chamber.

In an advantageous embodiment of the invention, the at least one end wall is provided with a substantially radially oriented groove or cutout just before the minimum position after bottom dead center, and the cutout is arranged so that the vane can rotate in this range of rotation. traced by the hook chamber during immersion.

The vane pump according to the invention is preferably used as a vacuum pump, for example for brake boosters or brake boosters, especially in fuel-injected motor vehicles.

The advantage in this case is that, despite the large delivery capacity, a very compact construction is obtained and, according to the invention, the power losses are low.

When used as an air or vacuum pump, further means are provided to enable a "cold start" of the pump. The problem with a "cold start" is the viscosity of the lubricating oil. Furthermore, when the engine is stopped, impurities in the oil become stuck, which impedes the movement of the vanes.

To avoid this, on the stem foot of the vane or on the underside of the hook head, a spring with a limited amount of action is placed in the hook chamber, which allows only the minimum position and the possible ν before and after this minimum position. It is preferable to elastically push both vanes apart within a slight rotation range. The spring used is, in particular, a Nonoimetal spring, which is designed to plunge into the hook chamber in cold conditions.

It is also possible to carry out a cold start by charging both hook chambers or one hook chamber, which sinks into the guide slot of the rotor, with pressurized oil.

In a preferred embodiment of the invention, the vane pump serving as a vacuum pump is pressurelessly lubricated with lubricating oil. However, in that case a valve arrangement is provided which closes in cold weather. This effect can be obtained, for example, by a cold length contrast or by a metal effect.

In another embodiment of a pump lubricated by lubricating oil, the pressure of the lubricating oil is utilized to extrude the vanes from the end position. In this case, the pump is used in particular as a vacuum valve for driving a brake booster of a fuel-injected motor vehicle or a servomotor connected to the lubrication system of the engine.

. . X□77' T %, 777. −2□ 1,
1 and the vanes are designed such that the hook chamber retracts into the guide slit of the rotor in the rotation range f between 90 degrees forward of the bottom dead center and the ridge angle 900 of the bottom dead center. This rotation range fhook chamber is connected via an oil supply conduit to a source of lubricating oil, in particular to a lubricating oil source. For this purpose, a disc-shaped cut □ is made on the end face of the rotor or the end face of the casing, as described in -f.
A notch is provided, an oil supply passage opens in this notch, and the oil supply hole is advantageously connected to the hook chamber after the hook chamber is recessed into the guide slit of the rotor. are arranged coaxially with respect to each other. In this construction, lubricating oil is sucked into the pump chamber under low pressure.

Furthermore, in vacuum pumps of this type, the discharge chamber □ is also provided with a check valve, so that the discharge chamber is likewise under vacuum at any time until an external pressure is established in the discharge chamber by suitable compression. All configurations reduce vacuum pump power requirements.

This is because when the vane turns orange, there is a significant pressure difference acting on both sides of the vane. However, this creates the risk that oil will be sucked into the discharge chamber. The oil requirement of the pump therefore increases'.

This leads to oil starvation in other lubrication points of the automobile engine. This is especially true when the engine is running at high rpm.
This occurs when the pump creates an unnecessarily large vacuum.

In order to limit the oil supply and obtain adequate oil flow, the stems of both vanes are provided with recesses that extend from the stem foot over the radial length of the vanes. , due to the overlap between this recess and the oil supply hole coaxial with the rotor, the oil flow between the oil supply 5 and the hook chamber is controlled by the cooperation between the edge of the recess and the oil supply hole. It is also possible to control the rotational position of the rotor depending on the rotational position of the rotor.

In this way, the oil pressure can be increased without causing unnecessarily high contact pressures that accelerate wear and waste power, as well as undesired oil spills in the suction or discharge chambers or in the oil tank of the engine. The hook chamber can be loaded with oil so that the protrusion movement of the vane can be fully supported. □ The concave portion of the vane is such that the connection between the oil supply hole and the hook chamber is controlled to open immediately after the hook chamber enters the guide slit of the rotor, and is controlled to close immediately before the hook chamber protrudes from the guide slit. It is designed to

The recess is advantageously formed as a recess in one or both end faces of each vane. Similarly, this notch may be formed in the back of each vane on the side opposite the hook head. A cutout may be formed in one or both edges of each vane from the stem foot of the vane over a radial length of the vane without acting on a crimp force that brings the vanes into contact with each other. .

As already explained, the oil supply hole can be provided in the casing end wall coaxially with respect to the rotor. In this embodiment, it is advantageous if the rotor is provided with an oil supply hole which also has a diameter that is large compared to the slit width of the guide slit of the rotor. In this way, a half-moon shaped passageway is formed on each side of the vane pair. Notch or cut to communicate.

This notch on the edge of the vane allows for a properly designed lap between the notch and the oil supply hole to control the amount of oil supplied to the hook chamber. Due to the continuous light design of the O-clap, it is possible to control the flow of oil from the first hole into the casing.Specifically, the cut-outs of both vanes are connected to the O-para horn at the dead center position of the vane. In the dead center position of both vanes, one hook chamber completely protrudes from the rotor. In this position, the vanes lie opposite each other across their entire width, so that the cutouts do not overlap each other. This prevents a connection between the oil supply conduit and the protruding hook chamber.

1" supply hole and p -77p",=0 between o enough"" 1.
(In order to obtain a loop effect, the seven chambers must recess into the guide slots of the rotor before an overlap between the cutout or cutout and the oil supply hole occurs. This is advantageously done before the corner 150. must be done.

The oil trapped in the hook chamber must not be prevented from flowing into the casing, in particular into the discharge chamber, upon protrusion of the hook chamber from the guide slot of the rotor. This oil spill is necessary to lubricate the vanes to the casing and rotor. However, it is necessary to prevent this oil from returning from the outlet into the crank chamber of the engine. This is because, on the - side, the outflow of this amount of oil from the outlet, especially the discharge valve, leads to a significant loss of output; on the other side, the high oil consumption of other actuators causes the oil pump to have insufficient delivery capacity. Particularly in some cases, such leakage of lubricating oil is disadvantageous.

According to the invention, therefore, the end wall of the casing is provided with a curved groove at the end of the discharge chamber. This groove is
A periphery is provided which extends over a part of the discharge chamber 9, preferably across the end region of the discharge chamber. This circumference mates with the part of the discharge chamber located behind the end of the outflow hole.

Due to the construction and for reasons of sufficient sealing, the outlet hole cannot reach its dead point. Therefore, the outermost end of the discharge chamber becomes a dead space. The groove further has a radial branch which extends from the circumferential end immediately before the oil supply. This radial branch is primarily limited by the dead center plane. The groove further has a connecting branch, which extends from the end of the radial branch approximately parallel to the circumference, the end point of which lies at an angle of 300, preferably 300, in front of the dead point line. It is located at a larger angle, preferably at an angle of 30° to 600° (measured from the center of the rotor).

Through the circumferential, radial and connecting branches of this groove, and through the cutout of one vane approaching the top dead center, the end region of the discharge chamber is filled with oil on the approach of the other vane to the bottom dead center. Connected to the supply section. As a result, the remaining oil in the discharge chamber is forced out through this groove to the oil supply. The depth of the groove is relatively small; moreover, the groove has a significant bend between the circumferential inner core and the radial core, which results in a significant constriction effect. This prevents on the negative side an excessive flow of oil from the oil supply into the discharge chamber while the discharge chamber is under negative pressure, and on the other side prevents oil from collecting in the end area of the discharge chamber. Oil is forced into the oil supply through the groove when the oil pressure in the oil supply is reached. Once extruded, the oil is used again to lubricate the reservoir of the vane's ejection movement.

Example The invention will now be described in detail with reference to the illustrated embodiments.

In the embodiment shown, a rotor 2 is rotatably mounted in the housing 1 . Rotor 2.111'3'-
``194 out 1''re@3uZyr<I.

It is driven by the camshaft of an engine, such as a car engine. The rotor is divided over its entire width by guide slits 4.

Two plates 75 and 6 are slidably guided within this guide sling 4. The cross sections of the vanes 5 and 6 are formed into a hook shape. Each vane has a stem 9, 10 and hooks 7, 8, the hooks being twice as thick as the stem.

The vanes 5, 6 are slidably positioned next to each other with their stems 9, 10. In order to prevent the stems from sticking together, especially during a cold start, both or one of the stems is provided with a cutout over its entire or partial width. The radial dimensions of this notch are designed such that the notch does not protrude from within the rotor guide slat 4 in any rotational position of the rotor. In short, this notch allows the end wall 11 of the casing 1 to be in any rotational position. ．． 12.

The shapes of the vanes 5 and 6 are completely identical to each other. 1st
Rotor rotational position shown in Figures and Figure 3 - 1 ( indicates the maximum position of the rotor. At this maximum position, the total length in the radial direction from the hooks of one vane to the hook head of the other vane is Maximum. - This total length is equal to the diameter of the inner wall of the casing 1.

In the maximum position shown, the vanes 6 reach their radially innermost position (bottom dead center) relative to the rotor. The vanes 5 reach their radially outermost position (top dead center). In this position, therefore, the hook chamber (the space between the hooks of one vane and the stem foot of the other vane) has a maximum volume. The rotor rotational position or vane position shown in broken lines in FIGS. 1 and 3 indicates the minimum position.

In this minimum position, the total length of both vanes in the rotor radial direction is at a minimum due to the eccentricity of the rotor 2 relative to the casing. Therefore, in this position the hook chamber 15.1.15
．． The volume of 2 is also the smallest.

The radial length of the hooks 7, 8 and the radial length of the stem 9°100 are such that the hook chamber 15 has the smallest possible volume in its minimum position, in other words the hooks 7 of each vane , 8 lower end 13 of each vane stem 9. It is designed so that it hardly touches the stem foot 14 of the IO.

Furthermore, in both exemplary embodiments, the inlet 32 and the outlet 33 are each closed in the counter-flow direction by a check valve 34,35. This prevents a backflow of oil into the inlet for the inlet 32 and provides a power reduction for the outlet.

According to the invention, the radial length of the hooks and the radius of the rotor are designed such that the minimum position range f of the lower edge 13 of the hook head is completely recessed into the guiding slit of the rotor. This means that, beyond the minimum position, the hook chamber is located in the rotor's guide sill (4) as well as in the end wall (11) of the casing. ”
Kure means closed by 12.

Furthermore, according to the present invention, the hook chamber is filled with oil on the way from the minimum position to the maximum position, and this oil is pushed out through the throttle between the maximum position (bottom dead center) and the minimum position. Ru.

For this purpose, in the embodiment shown in FIGS. 1 and 2, a crescent-shaped groove 16.17 is provided in each end wall 11, 12, which groove can be connected via a conduit 1'8.19. and is connected to an oil source 20. Is this oil under extremely low pressure? Used as a lubricating oil in other parts of the engine. The grooves 16 and 17 are connected to the hook chamber 15 when the rotor rotates.
It is designed to be traced by Groove 16.1
7 increases from the minimum position to the bottom dead center and then decreases again from the bottom dead center to the next minimum position range. Immediately before this minimum position, the groove cross section is widened to form an outflow area 21.

The action is as follows. When the rotor 2 and the vanes rotate in the direction shown by the arrow 22 starting from the minimum position shown by the broken line, the volume of the hook chamber 151 recessed in the guide sling 4 of the rotor 2 increases from the minimum position to the bottom dead center. increase

In this range of rotation, the hook chamber is traced by grooves 16, 17, from which oil is sucked. At the bottom dead center, the corresponding vane 5 reaches the dead center position, which is the innermost position with respect to the rotor 2. The volume of the hook chamber 9 gradually decreases after the bottom dead center, and the oil in the hook chamber flows into the groove 16.
17. Due to the relatively narrow cross section of the grooves 1.6.17, the escaping oil is throttled and the pressure in the hook chamber is adjusted to a pressure sufficient to push the vane 5 radially outward from its bottom dead center position. Ru.

At a minimum angle 10' to 200 after bottom dead center, the hook chamber is connected to the outflow region 21, where the pressure in the hook chamber drops sharply. This avoids unnecessary forces acting on the protruding vanes. The above functions occur similarly for the vane 6 and the hook chamber 15.2. By suitably shaping the groove cross-section, the pressure history in the hook chamber and thus the crimping force that presses the vane outwards can be optimally adjusted. This pressure history must be designed specifically in relation to the center of gravity of the vane.

According to the invention, the center of gravity of the vanes is adjusted by embedding a weight insert 23, for example a metal rod, in each hook head. As a result, by designing the shape i.1 of the heavy shear insert and the mass distribution so that the center of gravity does not exceed the center axis 24 of the rotor even at the bottom dead center position of each vane 5, 6. The center of gravity can be determined.

According to the present invention, the vane is inserted so that the hook chamber faces forward when viewed in the vane movement direction. In this way, the pressure acting on the upper and lower surfaces of each hook head on the pump discharge side is compensated, and the radial protrusion movement of the vanes is supported by negative pressure on the pump suction side.

In the embodiment shown in FIGS. 3 and 4, oil is supplied through a disc-shaped recess 2G provided on the end surface of the rotor 2. In the embodiment shown in FIGS. The recess 26 is sealed against the circumferential surface of the rotor 2 by a radial web 27 . The recess 26 communicates with an internal passage 29 of the hollow shaft 3 via an annular gap 28 . An oil supply conduit 30 opens into this internal passage 29 .

Oil is supplied into the internal passageway 29 by an oil supply conduit 30 . The diameter of this internal passage 29 is the same as that of the guide slit 4.
The width of the slit is large compared to the width of the slit, so oil can flow around both vanes. In FIG. 4, the position of the vane is indicated by a dotted line.

The guide sling 4 communicates with a notch 31 provided in the shaft 3. This notch 31 has a small length in the axial direction.

This cutout 31 allows oil to penetrate into the bearing area for lubrication of the bearing.

The recessed portion 26 is formed as a shallow notch that varies in depth in the radial direction. Each hook chamber 15.1 during rotor rotation,
15.2 sucks oil from the recess 26 between the minimum position and the bottom dead center, and pushes this oil out again between the bottom dead center and the next minimum position. When pushing out the oil, the oil flow is restricted because the recess 26 has only a small depth. Since the recessed portions 26 have different depths in the radial direction,
The aperture υ degree changes as it rotates.

Since the constriction effect hardly occurs in the region of greatest depth, the pressure in the hook chamber disappears again when the hook chamber passes through this region, i.e. just past the minimum position.

This loss of pressure before reaching the minimum position after bottom dead center is caused by the notch 3 provided on the front side of the hook head, as shown in Figure 3.
6 can also be used. This notch 36 connects the recess 26 of the rotor 2 to the circumference of the rotor (bypassing the web 27) in a narrow area before the minimum position where complete pressure relief is desired. This means is used alternatively for the annular recess of the recess 26.

It is known from experience that the viscosity of the lubricating oil increases significantly during cold starts of vacuum pumps, particularly at temperatures below 0°C. There is therefore a risk that the movement of the vanes will be blocked and that no pumping action will occur.

In vacuum pumps of this type, which are used, for example, in brake boosters, failure to function has serious negative consequences.

According to the invention, as a remedy in such a case, in the embodiment shown in FIGS. 1 and 2, pressurized oil is supplied for a short time via the conduit 20. -0 pressure''1''
The zero pressure magnitude of is sufficient to force the par' outwardly against the casing wall. A suitable thermo-valve may be provided for this pressure loading of the oil. In the embodiment shown in FIGS. 3 and 4, a ring 47 is inserted into an annular groove 48 provided in a hollow shaft 3 as a thermovalve of this type. In cold weather, the ring 7 narrows, the flow cross-section between the outer circumference of the oil supply conduit 30 and the inner circumference of the internal passage 29 decreases, and a pressure builds up in the internal passage 29. Details of this are illustrated in FIGS. 5, 6, 7 and 8. As shown in FIGS. 6 and 7, the ring 47 is cut at one location. The cut end surfaces of the ring 47 are formed in a step shape so as to overlap each other. The ring 47 has an annular, highly temperature-sensitive metal insert 39 on its inner periphery.
As shown in FIG. 6, a portion thereof has a slit, and as shown in FIG. 8, it is fixedly connected to a ring 47 by positive engagement.

97''47 itself''i7-4 sensitivity'Material/Example 1 8
, (slightly lower than the metal insert 39 in cold weather)
or made of non-shrinkable plastic. metal insert 3
Since the cooling contraction of 9 is large, the diameter of the ring 47 is reduced due to the )9 immetal effect. This reduces the gap between the inner circumferential surface of the internal passage 29 and the outer circumferential surface of the oil supply conduit 30, thereby creating oil pressure within the internal passage 29.

When heated, the inner diameter of the ring 47 increases, allowing the oil to flow out from the inner passage 29 without being throttled.

The embodiment shown in FIGS. 9 and 10 is a hook vane pump that operates both as a vacuum pump and as a hydraulic pump. The pump can be used to drive pneumatic cassada actuators, such as brake boosters, as well as hydraulic actuators, such as motor vehicle level controls. This pump, shown in cross section in FIG. 9, corresponds approximately to the pump shown in FIG.

A rotor 2 is eccentrically supported within a casing 1,
The rotor is driven by shaft 3 in the direction of rotation indicated by arrow 22.

Both vanes of the pump are slidably guided relative to each other in guide slots of the rotor. The vane is formed into a hook shape. The ends of each vane have a thickness equal to the sum of the thicknesses of the stems 9 and 10 that slide into each other.
This forms hook heads 7 and 8.

In the embodiment shown in FIG. 10, each hook head is attached to a bearing shell 4.
0, this bearing □Inside the shell 0 there is a roller 38.
is rotatably and slidably supported. This bearing shell is connected to the respective hook chamber 15.1 by means of pressure compensation channels 39a arranged one after the other in the axial direction.
15.2! It is connected to the.

When the rotor rotates in the direction shown by arrow 22, hook chamber 1
5.1 is inserted into the guide slit 4 of the rotor at or just before the minimum position (corner 9oO position) shown by the dotted line. The hook chamber 15.1 therefore forms a closed chamber after this minimum position. As the rotor rotates further, this closed hook chamber 15.1 is first connected to the inlet groove 37 up to bottom dead center and then to the outlet groove 45 behind the bottom dead center.

This outflow groove 45 extends between the bottom dead center and the next minimum position, and the hook chambers 151, 15.2 do not connect the outflow groove and the inflow groove at the bottom dead center.

The inflow and outflow channels are located within the flow circuit of the actuator, which is schematically illustrated in FIG. The flow circuit of the actuator 42 includes a controllable valve 43, a tank 44 and a pressure control valve 4.
6.

The inflow groove forms the suction side of a hydraulic pump connected to the tank 44. The hook chamber gradually increases in volume between the minimum position and the bottom dead center to suck in oil. In the next rotation range, that is, between the bottom dead center and the next minimum position, as the volume of the hook chamber gradually decreases, oil is forced out of the hook chamber, pressurized, and conveyed to the actuator 42. A pressure control valve 46 is arranged between the actuator conduit connected to the outflow groove and the tank conduit leading to the inflow groove, and this pressure control valve has a hook head that is always fully connected to the casing wall 11. A suitable pressure is set in such a way as to ensure contact with and thus sliding along the casing wall 1 without unnecessarily high friction.

In the embodiment shown in FIGS. 11, 12, 13 and 14, a rotor with a shaft 3 is rotatably mounted in the housing 1. In the embodiment shown in FIGS. The rotor and shaft are integrally molded. The shaft and rotor are provided with internal passages 29. This internal passage 29 is connected to an oil supply conduit. The oil supply conduit is connected to a lubricating oil pump (not shown). Oil supply conduit 30 is sealed to internal passage 29 by ring 47 . The ring 47 is an annular groove 4
It is fitted in 8. In cold conditions, ring 47
narrows the flow cross-section between the outer circumferential surface of the oil supply conduit 30 and the inner circumferential surface of the internal passage 29 , thereby reducing the internal passage 29
Pressure builds up within. Details of this have been explained with reference to FIGS. 5 to 8. 1a6o' The bellotor is provided with a guide slit 4 in the neutral plane. The slit width of this guide slit 4 is equal to the sum of the thicknesses of the vanes 5 and 6. The diameter of the internal passage 29 is large compared to the gap width of the guide passage. This creates half-moon-shaped channels on both sides of the vanes 5, 60 guided in the guide slits, which channels extend through the rotor along both sides of the vanes. Both bars 75.6 have hook heads 7,8 and stems 9,10.

The stems are formed to the same thickness. The hook head is equal to the thickness of both stems. The lower edge 13 of each hook head 7.8 together with the stem foot 14 of the stem of the other vane forms a hook chamber 15.1 and 15.2. The pump has an inlet 32 closed by a check valve and an outlet 33 likewise closed by a check valve. As shown in FIGS. 14A and 14B, the outflow port 33 is formed as a long hole closed in the outflow direction by a leaf spring 49. The leaf spring 49 is fixed by a screw 50 at its rear end when viewed in the direction of rotation. As a result, this leaf spring 49 has the function of a check valve.

As can be seen in Figures 12A and 12B, the vane stem is provided with cutouts 50 on either side of its ends. This cutout extends from the end of the stem foot 14 towards the hook head. As shown in FIG. 12B, a notch 51 may be provided in place of this cutout, and this notch 51 extends from the stem foot 14 toward the hook head.

By suitably designing the depth of the cutout or notch, the flow resistance of the oil flow, which will be described below, is determined.

13A, 13B and 1 of the vane, in particular its hook heads 7, 8 and its cut-outs and other details.
3C and 13E will be described below.

The line indicated by T in the drawing is the dead center plane. The axes of the casing 1 and the rotor 2 are located on this dead center plane. Further, the rotor is in close contact with the casing on this dead center plane. 13th
In the rotational position of the rotor 2 shown in Figure C, the vanes 5 and 6 are located in the direction of the dead center plane, the vane 6 is completely immersed in the rotor's guide slit (bottom dead center), and the vane 5 is in the direction of the dead center plane. It protrudes the most from the rotor (top dead center).

In the drawing, a plane passing through the rotor center point and perpendicular to the dead center plane T is designated by the symbol E. In the present invention, this position is called the minimum position or 9oO position. In this minimum position, the distance between the hook heads 7.8 of both vanes 5, 6 is at a minimum, as can be seen from FIG. 13E.

The direction of rotation is indicated by the reference numeral 22 in all figures. Both hook chambers must be oriented in the direction of rotation.

In the rotational position shown in FIG. 13A, the hook chamber 15 formed between the hook head and the stem 10 of the other vane 6
．． 2 is completely immersed in the guide slit Φ of the rotor. The hook chamber 15.2 communicates with the internal passage 29 via a cutout 50 in the stem 10. The hook chamber 152 is thereby loaded by the pressure of the lubricating oil in the internal passage 29. On the other side, the stem 9 of the vane 5 closes the internal passage 29 and thus the internal passage 29 and the hook chamber 1.
5.1 will be disconnected.

As can be seen from FIG. 11, the end wall of the casing is provided with a bent groove 53, the depth of which is 1 to 2 wn. This groove has circumferential branches 54,
This circumferential branch 54 has an extrusion chamber in the direction opposite to the arrow 22 from the dead point plane T. The end of this circumferential branch 54 facing the extrusion chamber overlaps the end of the outlet 33 provided in the opposite casing wall in the circumferential direction.

The groove 53 further has a radial plate 55 .

This radial plate lies along the dead center plane T and extends immediately before the internal passage 29 of the shaft 3 or rotor 2. Furthermore, the groove 53 is provided with a connecting branch 56, which connects the circumferential branch 5.
4 and is also oriented in the opposite direction to arrow 22.

□□3Affl, □3B□, □□3C, □3rd ・
, (As can be seen from Figure E, the connecting branch 56 and the radial plate 55 of the groove 53 are connected to each other to form a flat notch as shown by the dashed line.The circumferential branch 54 and the radial plate 55 need not be integrated into a common flat incision, since at the intersection of both branches a significant strangling effect occurs. This strangling effect is particularly important for the function of this groove. .

In FIG. 13A, the cutout of the bay 76 is connected to the connecting branch 56. This results in a connection between the end region of the extrusion chamber and the internal channel 29. This end region is located between the vane 5 and the dead center plane T. If there is still a negative pressure in the extrusion chamber, which is connected via the outlet 33 and the check valve 34 to the crankcase of the motor vehicle engine, or via the outlet 33, both the valves 75°6 In particular, the radial plate 55 is used insofar as a connection between the chamber and the extrusion chamber, which is restricted and also loaded with negative pressure, occurs.
Due to the strong constricting action of the groove 53 at the bend between the inner passage 29 and the circumferential branch 54, only a small amount of oil flows into the extrusion passage from the internal passage 29. In particular, the lubricating oil pressure in the internal passages is maintained. On the other hand, the groove 53 allows the oil or oil-air mixture in the extrusion chamber to flow into the internal passage 29 as soon as a pressure builds up in the extrusion chamber, which becomes significantly smaller.
pushed back inside. In the case 6, the connecting branch 56 and the cutout 5
Since the ゜to, t-shape becomes larger, the throttling effect of the oil supply is reduced.

As the rotor continues to rotate as shown in FIG. 13B, the connection between the extrusion chamber and the outlet 33 is cut off. The oil in the extrusion chamber flows through the groove 53 and the cutout 50 into the internal passage 2.
Pushed out into 9.

Communication between the extrusion chamber and the internal passage 29 is cut off for the first time at the dead center position shown in FIG. 13C. This is because the rear wall of the radial plate lies approximately in the dead center plane and the stem 9 of the vane 6 completely closes the radial plate. On the other side, the hook chamber 15.2 is connected to the internal passage 29. The pressure of the lubricating oil therefore acts on the vane 6 in the direction of protrusion during subsequent rotation. This is an extremely important effect.

This is because the vane 5 is in its inner dead center position and the centrifugal forces are therefore significantly compensated between one end with the hook head 8 and the other end with the stem 9, so that the direction of the protruding movement This is because only a very small centrifugal force acts on the By connecting the hook chamber 15.2 with the internal passage according to the invention, undesired conditions are compensated and lubricating oil pressure is available to support the protrusion movement of the vane.

As the rotor rotates further, the hook chamber 152 protrudes from the rotor guide sill 4 immediately after passing the minimum position, as can be seen in FIG. 13E. At this moment, the stem 10 of the vane 6 completely closes off the internal passage 29 again, so that the pump chamber or hook chamber 15.2 and the internal passage 29
and are no longer connected by the cutout 50.

As can be seen from FIG. 13D, just before the minimum position the hook chamber 15.1 retracts into the guiding slit of the rotor, immediately after which the stem lO of the vane 6 passes through its notch 51 into the internal passage 29. and the hook chamber 15.1.In short, the stem foot 14 of the vane 5 is loaded by the pressure of the lubricating oil, so that the protruding movement of the vane 5 is supported by the pressure of the lubricating oil.

What is important is that if the control edge of the hook head and the control edge of the cut-out cause connection of the oil pressure and dissipation of the oil pressure at the desired time, the immersion and pressure loading of one hook chamber 15.1 will be prevented. In addition, the protrusion of the other hook chamber 15.2 takes place in a time-fixed sequence, preferably without any time play.

[Brief explanation of the drawing]

FIG. 1 is a cross-sectional view of the first embodiment of the present invention, and FIG. 2 is a cross-sectional view of the first embodiment of the present invention.
A sectional view taken along the line ■-■ in the figure, FIG. 3 is a cross-sectional view taken along the line III-I [
FIG. 4 is a sectional view similar to FIG. 2 of the second embodiment of the present invention, FIG. 5 is a view based on the present invention, and FIG. 8 is a sectional view taken along the line ■-■ in FIG. FIG. 9 is a cross-sectional view of the third embodiment of the present invention, FIG. 10 is a partial cross-sectional view of the second embodiment of the present invention, and FIG.
The figure is a sectional view taken along the line ■-■ in Figure 9, Figure 12A is a perspective view of the vane according to the present invention, Figure 12B is a perspective view showing the back side of Figure 12A, and the figure is an outflow according to the present invention. A detailed view of the valve and FIG. 14B is a cross-sectional view taken in the direction indicated by the arrow in FIG. 14A. 1...Casing, 2...Rotor, 5...Shaft, Cow...Guidance! Jt, 5, 6... Vane, 7, 8...
Hook head, 9, 10... Stem, 11, 12... End wall, 13... Lower edge, 14... Stem foot, 15.1,
15°2...Hook chamber, 16. i7...groove, 18,
19° Conduit, 20 Oil source, 21 Outflow range, 22 Arrow, 23 Weight insert, 24
... central axis line, 25 ... solid axis line, 26 ... recessed part,
27... Web, 28... Annular gap, 29... Internal passage, 3o oil supply conduit, 31... Notch, 32...
・Inlet, 33...Outlet, 34.35...Check valve, 36...Notch, 37...Inflow groove, 38...
Roller, 39... Insert, 39a... Pressure compensation passage, Cow○... Bearing shell, 41... Actuator oil circuit, 42... Actuator, 43... Valve,
44... Tank, Cow 5... Outflow groove, 46... Pressure control valve, 47... Ring, 48... Annular groove, 49...
・Plate spring, 5o... Cutout, 51.52... Notch, 5
3... Groove, 54... Circumferential inner core, 55... Radial same, 56... Connecting branch. (1 other person) - Fig. 2; 11 to 1-shi

Claims (1)

[Scope of Claims] 1. A vane pump comprising a pair of hook-shaped vanes slidably arranged in parallel with each other in a guide slit of a rotor, the hook head of each vane and both Both stems of the vanes located side by side have a thickness adapted to the slit width of the guide slit, and a hook chamber is formed between each stem foot of one vane and the hook head of the other vane. is formed, and this hook chamber is recessed into the guide slit of the rotor over a partial rotation range of the rotor.
) is carried out within the rotation range between the bottom dead center curve angle 900 and the bottom dead center withdrawal angle 9000, and each hook chamber (15) is partially rotated from the bottom dead center curve angle 900 to the bottom dead center. Filled with oil, and the ridge angle from the bottom dead center to the bottom dead center is 900
A vane pump characterized in that it is opened via a throttle when partially rotated up to. 2. Claim 1, in which the cross-sectional area of the aperture is enlarged over the partial rotation between the bottom dead center and the bottom dead center ridge angle 900.
Vane pump as described in section. 3. The vane pump according to claim 2, wherein the expansion of the cross section of the throttle occurs rapidly just before the bottom dead center ridge angle 900. 4. A vane pump as claimed in claim 3, in which the cross-section of the choke is enlarged by a short radial notch (36) formed in the front side of the hook chamber. 5. The vane bon f according to any one of claims 1 to 3, wherein the oil supply portion to the hook chamber is connectable to a pressure oil source. 6. The vane pump according to any one of claims 1 to 5, wherein the oil inlet and oil outlet are open into a pressureless system. 7. The vane pump according to claim 1, wherein the oil inlet and the oil outlet are located in a hydraulic circuit equipped with a hydraulic actuator that produces a throttling. 8. The hook head (7, 8) is abutted against the casing wall by a roller, and the bearing shell (30) of the roller connects each hook chamber (15, 1,
15, '2), the vent pump according to any one of claims 1 to 7. 9. An oil inlet (16) is provided in one end wall along the rotation circle of the hook chamber, and this oil inlet extends between the minimum position and the bottom dead center in front of the bottom dead center. and
9. The vane pump according to claim 7, wherein the oil outlet (21) extends from a position farther away from the bottom dead center by a distance greater than the thickness of the vane to a position at a corner 900. 10. The vane pump according to claim 1, wherein a temperature-dependent throttle valve is disposed in at least one of the light 10, the oil supply path, and the oil discharge path. 11. A vane pump comprising a pair of hook-shaped vanes slidably arranged next to each other in a guide slit of a rotor, the hook head of each vane and the two hook-shaped vanes arranged next to each other in a guide slit of a rotor. The stem has a thickness adapted to the slit width of the guide slit, and a hook chamber is formed between each stem foot of one vane and the hook head of the other vane. In a type in which the hook chamber is recessed into the guide slit of the rotor over a partial rotation range of the rotor, the retraction of the hook chamber (15, 1, 15, 2) is at a angle 900 before the bottom dead center and an angle 900 outside the bottom dead center. and during the partial rotation of the rotor (2) from 900 before the bottom dead center to the bottom dead center, each hook chamber (15
) is filled with oil and the oil supply passage (
29) Vane pump, characterized in that the continuation of the sound is interrupted before the rotor protrudes from the guide slit (4). 12. The stems (9, 10) of both vanes are recessed (50,
51, 52), each of which extends from the stem foot (14) over a radial partial length of the vane, and which recess is coaxial with respect to the rotor. Its edge, which traces the oil supply hole during temporary overlap with the oil supply hole (29), makes the flow of oil between the oil supply hole and the hook chamber dependent on the rotational position of the rotor (2). 12. The vane pump according to claim 11, wherein the vane pump is controlled by: 13. The connection between the oil supply hole (29) and the hook chamber (15, 1, 15, 2) by the edge of the recessed part (50-52) is connected to the hook chamber ( 15,
13. The vane pump according to claim 12, wherein the vane pump is controlled to open immediately after the hook chambers 1, 15, and 2) are retracted, and is controlled to close immediately before the hook chamber protrudes from the guide slit of the rotor. 14. The vane bonder according to any one of claims 11 to 13, wherein the recessed portion (25) is a notch provided on the back surface of each vane. 15. The recess (50, 51) comprises a cut-out formed in one or both edges of each vane, the cut-out extending from the stem foot (14) over a radial partial length of the vane. A vane bonder according to any one of claims 11 to 14. 16. An oil supply hole (29) is coaxially provided in the rotor, and the diameter of the oil supply hole (29) is larger than the width of the guide slit, and the notch or cutout is located The vane pump according to claim 14 or 15, wherein the oil supply hole extends into the rotor length region.17. Unwrapped Claim 16
Vane Bonde as described in section. 18. The retraction of the hook chamber is at an angle of 5° before the overlap between the notch or cutout and the oil supply hole starts in the rotation range before bottom dead center.
150. The vane pump according to any one of claims 11 to 17. 19. The end wall of the pump casing (1) is provided with a curved groove (53) with a circumferential branch in the discharge area, which circumferential branch forms part of the outlet chamber of the pump, in particular the outflow chamber. located in the end region of, in particular behind the end of the outflow channel (33),
Coupled with a portion of said end region, said groove further comprises a generally radially oriented radial branch (55), said radial branch being substantially limited by a deadfish plane. and extending from the end point of the outflow chamber to just before the radial oil supply section (29), said groove further comprising a connecting branch (56) parallel to said circumferential branch (54), which connection Branch (56) slow' I=4 TN, a#
M 30°-15-Z-7(7)161N. -8°50.51) Vane pump according to any one of claims 11 to 18 1. 20. The connecting branch (56) is formed by a radial branch extension extending in a direction opposite to the direction of rotation, and at least 45° forward of the dead center position between the end position and the dead center position.
↑The vane pump according to claim 19, which is connected to the cutout portions (50, 51) of the vane. 21. The vane pump according to claim 11, wherein the outflow passage (33) extending over a partial circumference is closed by a check valve (35).