CA2575778C - Single-blade vacuum pump - Google Patents
Single-blade vacuum pump Download PDFInfo
- Publication number
- CA2575778C CA2575778C CA2575778A CA2575778A CA2575778C CA 2575778 C CA2575778 C CA 2575778C CA 2575778 A CA2575778 A CA 2575778A CA 2575778 A CA2575778 A CA 2575778A CA 2575778 C CA2575778 C CA 2575778C
- Authority
- CA
- Canada
- Prior art keywords
- blade
- vacuum pump
- section
- peripheral surface
- blade vacuum
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
- F01C21/0881—Construction of vanes or vane holders the vanes consisting of two or more parts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F04C18/3441—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2220/00—Application
- F04C2220/10—Vacuum
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
The invention relates to a single-winged vacuum pump provided with a pot-shaped housing (12), a rotor (18) which is rotationally and eccentrically mounted in the housing, a wing (20) which is displacably mounted in the rotor and orthogonal on the rotational axis and a work chamber (22) which receives the wing (20) and which comprises an internal peripheral surface (30) whereon both of the sealing edges (68), which are arranged opposite to each other of the wing, are arranged. The wing (20) subdivides the work chamber into a suction chamber (30) and a pressure chamber and the end (28) of the wing, which is oriented towards the internal peripheral surface (30), comprises a flattened section (66) on the side oriented towards the pressure chamber (26).
Description
Title: Single-Blade Vacuum Pump Description The invention relates to a single-blade vacuum pump provided with a pot-shaped housing, a rotor which is rotationally and eccentrically mounted in the housing, a blade which is displacably mounted in the rotor and orthogonal on the rotational axis, and a expansion chamber which receives the blade and comprises an inner peripheral surface whereon abut the two sealing edges of the blade, which are arranged opposite to one other, wherein the blade subdivides the expansion chamber into an inlet chamber and a pressure chamber.
Vacuum pumps with this type of structure are known from (DE 100 46 697 A1). As a rule, they serve to provide vacuum users, for example, in motor vehicles, with vacuum in that the rotor is caused to rotate, and air is evacuated from the inlet chamber from an vacuum line via the intake arm. The expansion chamber of this vane pump is designed in such a way that the blade with its two ends, which are located opposite one another, moves along the inner peripheral surface. Further, the blade separates the inlet chamber, which is connected to the intake connection from the pressure chamber, which is connected to the pressure connection.
In order to achieve a high degree of efficiency, the blade must abut permanently on the inner peripheral surface, otherwise the inlet chamber will be ventilated.
Vacuum pumps with this type of structure are known from (DE 100 46 697 A1). As a rule, they serve to provide vacuum users, for example, in motor vehicles, with vacuum in that the rotor is caused to rotate, and air is evacuated from the inlet chamber from an vacuum line via the intake arm. The expansion chamber of this vane pump is designed in such a way that the blade with its two ends, which are located opposite one another, moves along the inner peripheral surface. Further, the blade separates the inlet chamber, which is connected to the intake connection from the pressure chamber, which is connected to the pressure connection.
In order to achieve a high degree of efficiency, the blade must abut permanently on the inner peripheral surface, otherwise the inlet chamber will be ventilated.
A known solution proposes that the blade be structured in two parts and that a spring be inserted between the two blade components, which forces the two blade components towards the outside in the direction of the peripheral surface. This ensures that the sealing edge of the blade permanently abuts on the inner peripheral surface. However, it is considered to be a disadvantage that, because of the contact pressure, the blade is subjected to considerable wear, as a result of which not only the efficiency of said blade diminishes, but also maintenance intervals are reduced as well.
From the DE 43 32 540 Al, a vane pump is known in which several blades are arranged eccentrically in the rotor. At the point and the base of said blade, said blades are pressurized with the pressure prevailing in the pressure chamber. From DE-PS 364 107, a lubricating device for fast running rotors is known in which the blade distributing the lubricant film is chamfered.
It is the object of the present invention to provide a single blade vacuum pump with improved efficiency.
In view of the foregoing, a single-blade vacuum pump of the aforesaid type is used to solve the problem in accordance with the invention in that the ends of the blade facing the inner peripheral surface comprise a flattened section facing the compression chamber.
Usually the ends of the blade are rounded cylindrically and via a central line of contact or surface line of the cylinder abut on the inner peripheral surface of the expansion chamber. With the single-blade vacuum pump according to the invention, the end of the blade is partially flattened on the pressure side as a result of which the blade is able to change effective pressure forces in their direction. Due to the flattened section, the radial component of the pressure force is increased, which counteracts the centrifugal force of the blade. The centrifugal force of the blade, which presses the blade against the peripheral surface of the expansion chamber therefore is reduced by the compression force counteracting said centrifugal force from the pressure chamber. The blade, therefore, is pressed with less force against the peripheral surface.
With the preferred embodiment, the flattened section is easily configured. This type of configuration of the blade end can be produced with relative ease because the flattened section, for example, can be attached and/or produced by means of a milling process.
In an improvement, the section comprises an angle to the longitudinal surface, which varies by 0 . Furthermore, eccentrically the blade abuts on the inner peripheral surface.
The line of contact also has a distance to the center plane of the blade, as a result of which the improvement is achieved that the flattened section can be larger. As a result, the tangential component of the compression force can be reduced even further.
With a preferred embodiment, it is provided that the section bordering on and/or the surfaces bordering on the section are partially cylindrical. This offers the advantage that the line of contact can move relatively easily along the surface of the point of the blade. Since the contact angle of the blade changes permanently during a complete rotation of the rotor, the line of contact of the point of the blade moves negligibly in which the cylindrical design of the point of the blade ensure even wear.
A harmonious course and, therefore, a simple production of the point of the blade is achieved in that the surfaces at the point of the blade continuously change into a flattened section.
Further, the surfaces and the section at the transfer points may comprise similar tangents. The processing tools are able to produce the point of the blade in one operating cycle and/or with an injection-molded point, the injection mold can be produced simply and at a low cost.
Preferably, the blade comprises a body and two terminal top parts. At said top parts, the flattened section is attached and said top parts abut on the inner peripheral surface of the expansion chamber. This has the major advantage that worn blades can be maintained by replacement of the top parts, wherein the top parts preferably are made of synthetic material, whereas the body of the blade, for example, is made of metal. Further, the body of the blade is a die-cast or injection-molded element, and the top parts are injection-molded.
For the purpose of attaching the top parts, the body of the blade comprises at its top parts the ends accommodating the top parts in a slot, which runs orthogonally towards the long side of the body of the blade. The top part comprises one of two parallel U-shaped or C-shaped cross-sections. Consequently, the top parts can be plugged in at various ends of the body of the blade, and are movable only in the direction of the longitudinal axis of the blade. As a result, owing to their centrifugal force, such top parts can abut on the inner peripheral surface of the expansion chamber and seal the inlet chamber opposite the pressure chamber.
With one embodiment, the limbs flank a fixed link, whereby the limbs themselves at their free ends are formed as a semi-circle, and engage in a corresponding semi-circular recess at the ends of the body of the blades. Both the fixed link and the recess for the limbs prevent the top parts from effecting undefined motions during the operation of the pump. In particular, this prevents shaking and rattling, and furthermore the development of noises is suppressed. In an improvement, the top parts are placed under minor initial stress force at the ends of the body of the blade.
Another characteristic feature is that when turning the top part by 1800, said top part can be rotated on the body of the blade.
This means that the ends of the body of the blade and the seat are so designed that they allow the top parts to be rotated.
Other advantages, characteristics, and details of the invention are specified in the subordinate claims and in the following description in which, by referring to the drawing, a preferred embodiment is described in detail. Further, the characteristic elements represented in the drawing and mentioned in the description and in the claims can be fundamental to the invention individually or in any combination.
Of the drawing:
Figure 1 shows an exploded view of the vacuum pump;
Figure 2 shows a perspective view of a single-blade vacuum pump and blade;
Figure 3 shows a perspective presentation of the body of the blade;
Figure 4 shows a perspective view of the top part; and Figure 5 shows a horizontal projection of one end of the blade, indicating the distribution of compression pressure.
Figure 1 shows the vacuum pump with the overall reference symbol wherein the housing 12 is represented without cover. The housing 12 has a suction connection 14, which ends in an interior 16. This interior 16 contains a rotor with the overall designation 18, wherein a blade 20 is rotatably mounted orthogonally to the axis of rotation 21.
As is evident from Figure 2, the blade 20 subdivides the expansion chamber 22, which is formed by the interior 18, into an inlet chamber 24 and a pressure chamber 26. Further, the blade with its two ends 28 abuts on one of the inner peripheral surfaces 30 surrounding the expansion chamber 22.
As is shown in Figure 1, the blade 20 is formed by a body 32 and two top parts 34. Figure 3 shows the body of the blade 32, wherein Figure 4 shows one of the top parts 34. In the embodiment, the body of the blade 32 is made of metal, and is a die-cast part, which however also may be injection-molded. For tribological reasons, the top part 34 is made of synthetic material and injection-molded. For the purpose of weight reduction and in order to reduce moments of inertia, the body of the blade 32 is provided with cavities 36, which are either continuous or are formed as blind holes. At its two ends 38, the body of the blade 32 respectively is provided with a slot 40, which extends not only in the direction of the longitudinal axis 42 of the blade 20, but also orthogonally towards the broadside surface 44. The longitudinal axis 42 of the blade 20 is located between the two broadside surfaces 44, and the line of contact 68 is located between the longitudinal center plane 70 and the broadside surface 44 facing the inlet chamber 42.
Furthermore, the two broadside surfaces 44 in the area of the ends 38 are essentially provided with semi-circular recesses 46 in which the limbs 48 (see Figure 4) of the top part 34 can be plugged. The two limbs 48 flank a fixed link 50, which also extends in the direction of the longitudinal axis 42 of the blade 20 and the form of a slot 40. Both the slot 40 with the fixed link 50 and the recess 46 prevent that the top part 34 from being displaced in the direction of the axis 52. The limb 48, which encloses the end 38, prevents that the top part 34 from abruptly giving way in the direction of the axis 54. This means that the top part 34 is merely fixed in the direction of the longitudinal axis 42, which is movable at the body of the blade 32.
Figure 5 shows a horizontal projection of the body of the blade 32 with mounted top part 34. Further, the top part 34 touches the inner peripheral surface 30, so that the inlet chamber 24 is located below and the pressure chamber 26 above the blade 20.
The blade 20 rotates in the direction of the arrow 56 and at its rear, facing in the inlet chamber 24, and an angle other than 900 goes over to the broadside surface 44 of the blade 20.
If the blade 20 comprises a rounded end 28, the axial compression force 58, which, for example, is created by the pressure in the pressure chamber 26, would have an effect on the end 28. Said compression force 58 acts against the centrifugal force of the blade 20, as indicated with the arrow 64.
As is shown in Figures 4 and 5, the top part 34 has a flattened section 66 upon which acts the compression force 60. Said compression force 60 is composed of the compression force 58 and an additional compression force 62, which is created because the line of contact 68 comprises a distance A to the center plane 70 of the blade 20. Since the compression force 60 actually attacking the blade 20 is greater than the compression force 58 with a conventional blade on account of the shift of the line of contact 68, and furthermore, the forces 74 created by the vacuum in the inlet chamber 24 are smaller then with a conventional blade, the contact pressure at the line of contact 68 is considerably reduced, which reduces wear.
Furthermore, it is evident that the line of contact 38 is located on a partial cylindrically shaped section 72 of the top part 34.
The partial cylindrically shaped section 72, maintaining the same tension, continues to the level section 66. This has the advantage that the lubricant on the pressure side of the blade 20 is distributed evenly over the section 66 and the section 72, so that the line of touch 68 is lubricated across its entire length.
From the DE 43 32 540 Al, a vane pump is known in which several blades are arranged eccentrically in the rotor. At the point and the base of said blade, said blades are pressurized with the pressure prevailing in the pressure chamber. From DE-PS 364 107, a lubricating device for fast running rotors is known in which the blade distributing the lubricant film is chamfered.
It is the object of the present invention to provide a single blade vacuum pump with improved efficiency.
In view of the foregoing, a single-blade vacuum pump of the aforesaid type is used to solve the problem in accordance with the invention in that the ends of the blade facing the inner peripheral surface comprise a flattened section facing the compression chamber.
Usually the ends of the blade are rounded cylindrically and via a central line of contact or surface line of the cylinder abut on the inner peripheral surface of the expansion chamber. With the single-blade vacuum pump according to the invention, the end of the blade is partially flattened on the pressure side as a result of which the blade is able to change effective pressure forces in their direction. Due to the flattened section, the radial component of the pressure force is increased, which counteracts the centrifugal force of the blade. The centrifugal force of the blade, which presses the blade against the peripheral surface of the expansion chamber therefore is reduced by the compression force counteracting said centrifugal force from the pressure chamber. The blade, therefore, is pressed with less force against the peripheral surface.
With the preferred embodiment, the flattened section is easily configured. This type of configuration of the blade end can be produced with relative ease because the flattened section, for example, can be attached and/or produced by means of a milling process.
In an improvement, the section comprises an angle to the longitudinal surface, which varies by 0 . Furthermore, eccentrically the blade abuts on the inner peripheral surface.
The line of contact also has a distance to the center plane of the blade, as a result of which the improvement is achieved that the flattened section can be larger. As a result, the tangential component of the compression force can be reduced even further.
With a preferred embodiment, it is provided that the section bordering on and/or the surfaces bordering on the section are partially cylindrical. This offers the advantage that the line of contact can move relatively easily along the surface of the point of the blade. Since the contact angle of the blade changes permanently during a complete rotation of the rotor, the line of contact of the point of the blade moves negligibly in which the cylindrical design of the point of the blade ensure even wear.
A harmonious course and, therefore, a simple production of the point of the blade is achieved in that the surfaces at the point of the blade continuously change into a flattened section.
Further, the surfaces and the section at the transfer points may comprise similar tangents. The processing tools are able to produce the point of the blade in one operating cycle and/or with an injection-molded point, the injection mold can be produced simply and at a low cost.
Preferably, the blade comprises a body and two terminal top parts. At said top parts, the flattened section is attached and said top parts abut on the inner peripheral surface of the expansion chamber. This has the major advantage that worn blades can be maintained by replacement of the top parts, wherein the top parts preferably are made of synthetic material, whereas the body of the blade, for example, is made of metal. Further, the body of the blade is a die-cast or injection-molded element, and the top parts are injection-molded.
For the purpose of attaching the top parts, the body of the blade comprises at its top parts the ends accommodating the top parts in a slot, which runs orthogonally towards the long side of the body of the blade. The top part comprises one of two parallel U-shaped or C-shaped cross-sections. Consequently, the top parts can be plugged in at various ends of the body of the blade, and are movable only in the direction of the longitudinal axis of the blade. As a result, owing to their centrifugal force, such top parts can abut on the inner peripheral surface of the expansion chamber and seal the inlet chamber opposite the pressure chamber.
With one embodiment, the limbs flank a fixed link, whereby the limbs themselves at their free ends are formed as a semi-circle, and engage in a corresponding semi-circular recess at the ends of the body of the blades. Both the fixed link and the recess for the limbs prevent the top parts from effecting undefined motions during the operation of the pump. In particular, this prevents shaking and rattling, and furthermore the development of noises is suppressed. In an improvement, the top parts are placed under minor initial stress force at the ends of the body of the blade.
Another characteristic feature is that when turning the top part by 1800, said top part can be rotated on the body of the blade.
This means that the ends of the body of the blade and the seat are so designed that they allow the top parts to be rotated.
Other advantages, characteristics, and details of the invention are specified in the subordinate claims and in the following description in which, by referring to the drawing, a preferred embodiment is described in detail. Further, the characteristic elements represented in the drawing and mentioned in the description and in the claims can be fundamental to the invention individually or in any combination.
Of the drawing:
Figure 1 shows an exploded view of the vacuum pump;
Figure 2 shows a perspective view of a single-blade vacuum pump and blade;
Figure 3 shows a perspective presentation of the body of the blade;
Figure 4 shows a perspective view of the top part; and Figure 5 shows a horizontal projection of one end of the blade, indicating the distribution of compression pressure.
Figure 1 shows the vacuum pump with the overall reference symbol wherein the housing 12 is represented without cover. The housing 12 has a suction connection 14, which ends in an interior 16. This interior 16 contains a rotor with the overall designation 18, wherein a blade 20 is rotatably mounted orthogonally to the axis of rotation 21.
As is evident from Figure 2, the blade 20 subdivides the expansion chamber 22, which is formed by the interior 18, into an inlet chamber 24 and a pressure chamber 26. Further, the blade with its two ends 28 abuts on one of the inner peripheral surfaces 30 surrounding the expansion chamber 22.
As is shown in Figure 1, the blade 20 is formed by a body 32 and two top parts 34. Figure 3 shows the body of the blade 32, wherein Figure 4 shows one of the top parts 34. In the embodiment, the body of the blade 32 is made of metal, and is a die-cast part, which however also may be injection-molded. For tribological reasons, the top part 34 is made of synthetic material and injection-molded. For the purpose of weight reduction and in order to reduce moments of inertia, the body of the blade 32 is provided with cavities 36, which are either continuous or are formed as blind holes. At its two ends 38, the body of the blade 32 respectively is provided with a slot 40, which extends not only in the direction of the longitudinal axis 42 of the blade 20, but also orthogonally towards the broadside surface 44. The longitudinal axis 42 of the blade 20 is located between the two broadside surfaces 44, and the line of contact 68 is located between the longitudinal center plane 70 and the broadside surface 44 facing the inlet chamber 42.
Furthermore, the two broadside surfaces 44 in the area of the ends 38 are essentially provided with semi-circular recesses 46 in which the limbs 48 (see Figure 4) of the top part 34 can be plugged. The two limbs 48 flank a fixed link 50, which also extends in the direction of the longitudinal axis 42 of the blade 20 and the form of a slot 40. Both the slot 40 with the fixed link 50 and the recess 46 prevent that the top part 34 from being displaced in the direction of the axis 52. The limb 48, which encloses the end 38, prevents that the top part 34 from abruptly giving way in the direction of the axis 54. This means that the top part 34 is merely fixed in the direction of the longitudinal axis 42, which is movable at the body of the blade 32.
Figure 5 shows a horizontal projection of the body of the blade 32 with mounted top part 34. Further, the top part 34 touches the inner peripheral surface 30, so that the inlet chamber 24 is located below and the pressure chamber 26 above the blade 20.
The blade 20 rotates in the direction of the arrow 56 and at its rear, facing in the inlet chamber 24, and an angle other than 900 goes over to the broadside surface 44 of the blade 20.
If the blade 20 comprises a rounded end 28, the axial compression force 58, which, for example, is created by the pressure in the pressure chamber 26, would have an effect on the end 28. Said compression force 58 acts against the centrifugal force of the blade 20, as indicated with the arrow 64.
As is shown in Figures 4 and 5, the top part 34 has a flattened section 66 upon which acts the compression force 60. Said compression force 60 is composed of the compression force 58 and an additional compression force 62, which is created because the line of contact 68 comprises a distance A to the center plane 70 of the blade 20. Since the compression force 60 actually attacking the blade 20 is greater than the compression force 58 with a conventional blade on account of the shift of the line of contact 68, and furthermore, the forces 74 created by the vacuum in the inlet chamber 24 are smaller then with a conventional blade, the contact pressure at the line of contact 68 is considerably reduced, which reduces wear.
Furthermore, it is evident that the line of contact 38 is located on a partial cylindrically shaped section 72 of the top part 34.
The partial cylindrically shaped section 72, maintaining the same tension, continues to the level section 66. This has the advantage that the lubricant on the pressure side of the blade 20 is distributed evenly over the section 66 and the section 72, so that the line of touch 68 is lubricated across its entire length.
Claims (13)
1. A single-blade vacuum pump comprising a pot-shaped housing (12), a rotor (18) which is rotationally and eccentrically mounted in the housing, a blade (20) which is displaceably mounted in the rotor and orthogonal on the rotational axis, and an expansion chamber (22) which receives the blade (20) and comprises an inner peripheral surface (30) whereon abut the two sealing edges (68) of the blade, which are arranged opposite to one other, wherein the blade (20) subdivides the expansion chamber (22) into an inlet chamber (30) and a pressure chamber (26), wherein the end (28) of the blade (20) facing the inner peripheral surface (30) comprises a flattened section (66) and wherein the surfaces bordering onto section (66) are partially cylindrical.
2. A single-blade vacuum pump as defined in claim 1, wherein the flattened section (66) is even.
3. A single-blade vacuum pump as defined in claim 1 or claim 2, wherein the section (66) comprises an angle varying by 0° towards the longitudinal surface of the blade (20).
4. A single-blade vacuum pump as defined in any one of claims 1 to 3, characterized in that the blade (20) eccentrically abuts on the inner peripheral surface (30).
5. A single-blade vacuum pump as defined in any one of claim 1 to 4, wherein the line of contacts (68) of the blade (20) comprises a distance (A) towards the center level (70) of the blade (20).
6. A single-blade vacuum pump as defined in claim 1, wherein the surfaces continuously go over to the section (66).
7. A single-blade vacuum pump as defined in claim 1, wherein the surfaces and the section (66) at the transition points comprise similar tangents.
8. A single-blade vacuum pump as defined in any one of claims 1 to 7, wherein the blade (20) comprises a body (32) and two terminal top parts (34).
9. A single-blade vacuum pump as defined in claim 8, wherein the body of the blade (32) at its ends (32) accommodating the top parts (34) comprises a slot (40), which runs orthogonally towards the longitudinal broadside (44) of the body of the blade (32).
10. A single-blade vacuum pump as defined in claim 8 or 9, wherein the top part (34) comprises a U-shaped cross-section created by two parallel limbs (48).
11. A single-blade vacuum pump as defined in claim 10, wherein the limbs (48) flank a fixed link (50).
12. A single-blade vacuum pump as defined in claims 9 and 11, wherein with the mounted blade (20) the fixed link (50) engages in a slot (40).
13. A single-blade vacuum pump as defined in any one of claims 8 to 12, wherein the top part (34) turned by 180° can be plugged on the body of the blade (32).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102004034921.5 | 2004-07-09 | ||
| DE102004034921A DE102004034921B9 (en) | 2004-07-09 | 2004-07-09 | A single-blade |
| PCT/EP2005/004210 WO2006005381A1 (en) | 2004-07-09 | 2005-04-26 | Single-winged vacuum pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CA2575778A1 CA2575778A1 (en) | 2006-01-19 |
| CA2575778C true CA2575778C (en) | 2012-11-20 |
Family
ID=34964118
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA2575778A Expired - Fee Related CA2575778C (en) | 2004-07-09 | 2005-04-26 | Single-blade vacuum pump |
Country Status (6)
| Country | Link |
|---|---|
| EP (1) | EP1766237B1 (en) |
| KR (1) | KR101234491B1 (en) |
| CN (1) | CN100465448C (en) |
| CA (1) | CA2575778C (en) |
| DE (3) | DE102004064029B4 (en) |
| WO (1) | WO2006005381A1 (en) |
Families Citing this family (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102005015721B3 (en) * | 2005-03-31 | 2006-12-21 | Joma-Hydromechanic Gmbh | vacuum pump |
| DE102006016243A1 (en) | 2006-03-31 | 2007-10-04 | Joma-Hydromechanic Gmbh | Rotor pump`s e.g. vacuum pump, vane, has vane body comprising frame work structure with internal compartment walls transverse to longitudinal direction of vane, where internal compartment walls run in longitudinal axis |
| JP5302303B2 (en) * | 2007-07-03 | 2013-10-02 | オー・エム・ピー・オッフィチーネ・マッツォッコ・パッニョーニ・エス・エール・エル | Vacuum pump for automobile engine |
| DE102008002763A1 (en) * | 2008-02-01 | 2009-08-06 | Zf Lenksysteme Gmbh | Sliding vane pump, particularly for power steering of commercial motor vehicles, has rotor that consists of radially moving wing guided in slot, where wing forms wing head which with contact edge glides along inner contour of cam ring |
| DE102008019440A1 (en) | 2008-04-17 | 2009-10-22 | FRÖTEK Kunststofftechnik GmbH | Wing of a vane pump or vane compressor |
| KR100919253B1 (en) * | 2008-07-03 | 2009-09-30 | 한세구 | Twin cylinder pump |
| DE102009037277B4 (en) * | 2009-08-12 | 2016-02-04 | Schwäbische Hüttenwerke Automotive GmbH | Adjustable vacuum pump |
| EP2299055B1 (en) | 2009-09-14 | 2014-11-12 | Pierburg Pump Technology GmbH | Automotive vacuum vane pump |
| CN103850937B (en) * | 2012-11-30 | 2016-08-24 | 上海华培动力科技有限公司 | A kind of negative pressure device assisting automobile-used brakes |
| DE102015213098B4 (en) * | 2015-07-13 | 2017-05-04 | Joma-Polytec Gmbh | Wing for a vane pump and vane pump |
| CN105090035A (en) * | 2015-07-24 | 2015-11-25 | 裕克施乐塑料制品（太仓）有限公司 | Vacuum pump blade with oil grooves and vacuum pump |
Family Cites Families (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE364107C (en) * | 1922-11-25 | Walter Schindler | Lubricating device for high-speed rotating bodies | |
| DE198127C (en) * | 1906-02-09 | 1908-05-06 | Sealing of the piston of power machines with a rotating piston that can be moved in the piston drum by means of a wedge effect | |
| DE2047624A1 (en) * | 1970-09-28 | 1972-05-18 | Fa. Wilhelm Reich, 7900 Ulm | Vane pump |
| US4163635A (en) * | 1975-06-24 | 1979-08-07 | Nippon Piston Ring Kabushiki Kaisha | Vane type rotary fluid pumps or compressors |
| DE2945488A1 (en) * | 1979-11-10 | 1981-05-21 | Barmag Barmer Maschf | Vacuum pump for vehicle brakes - has rotor of sintered alloyed aluminium for light weight |
| US4957420A (en) * | 1988-04-27 | 1990-09-18 | Nippon Piston Ring Co., Ltd. | Vane pump with guide means for regulating movement of vane |
| IT1229927B (en) * | 1988-10-14 | 1991-09-16 | Cipelletti Alberto Cae | VANE PUMP. |
| JP2818207B2 (en) * | 1989-08-04 | 1998-10-30 | 株式会社日立製作所 | Rotating machine and refrigeration apparatus using the rotating machine |
| DE4332540A1 (en) * | 1993-09-24 | 1995-03-30 | Bosch Gmbh Robert | Vane pump |
| WO2000036303A1 (en) * | 1998-12-14 | 2000-06-22 | Mitsubishi Denki Kabushiki Kaisha | Vane type vacuum pump for automobiles |
| ATE250722T1 (en) * | 2000-03-15 | 2003-10-15 | Joma Hydromechanic Gmbh | DISPLACEMENT PUMP |
| DE10046697A1 (en) * | 2000-09-21 | 2002-04-11 | Bosch Gmbh Robert | Plastic blades for a vane vacuum pump |
| KR100426867B1 (en) * | 2001-08-09 | 2004-04-13 | 맹혁재 | compressor |
| KR100408152B1 (en) * | 2001-08-14 | 2003-12-01 | 주식회사 우성진공 | Cylinder structure of vacuum pump |
| DE10307040A1 (en) * | 2003-02-20 | 2004-09-16 | Luk Automobiltechnik Gmbh & Co. Kg | Vacuum pump, especially for power assisted vehicle braking system, includes vane having interior hollow spaces with closed injection holes |
-
2004
- 2004-07-09 DE DE102004064029A patent/DE102004064029B4/en not_active Expired - Lifetime
- 2004-07-09 DE DE102004034921A patent/DE102004034921B9/en not_active Expired - Lifetime
-
2005
- 2005-04-26 EP EP05731506A patent/EP1766237B1/en active Active
- 2005-04-26 WO PCT/EP2005/004210 patent/WO2006005381A1/en active IP Right Grant
- 2005-04-26 KR KR1020077003040A patent/KR101234491B1/en not_active IP Right Cessation
- 2005-04-26 CN CNB2005800271534A patent/CN100465448C/en not_active Expired - Fee Related
- 2005-04-26 DE DE502005002932T patent/DE502005002932D1/en active Active
- 2005-04-26 CA CA2575778A patent/CA2575778C/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| CA2575778A1 (en) | 2006-01-19 |
| WO2006005381A1 (en) | 2006-01-19 |
| EP1766237A1 (en) | 2007-03-28 |
| DE502005002932D1 (en) | 2008-04-03 |
| EP1766237B1 (en) | 2008-02-20 |
| DE102004064029B4 (en) | 2008-04-10 |
| DE102004034921B3 (en) | 2005-12-29 |
| DE102004064029A1 (en) | 2007-04-12 |
| CN101002023A (en) | 2007-07-18 |
| KR101234491B1 (en) | 2013-02-18 |
| KR20070034091A (en) | 2007-03-27 |
| CN100465448C (en) | 2009-03-04 |
| DE102004034921B9 (en) | 2006-04-27 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CA2575778C (en) | Single-blade vacuum pump | |
| US20150198161A1 (en) | Scroll type compressor | |
| CA2575780C (en) | Single-blade vacuum pump | |
| US9206690B2 (en) | Variable displacement pump | |
| KR20070034092A (en) | Single blade vacuum pump | |
| EP1703136B1 (en) | Lateral channel compressor | |
| MY119972A (en) | Oscillating piston type compressor and method of manufacturing piston thereof. | |
| US7503757B2 (en) | Oil pump having rotor receiving portion for restriction moving range of an outer rotor in a direction perpendicular to an eccentric direction | |
| US10683864B2 (en) | Twin vane rotary vacuum pump | |
| KR100590650B1 (en) | Vaccum pump for vehicle | |
| JP2003286979A5 (en) | ||
| WO2009090079A2 (en) | A displacement pump with a barrier against the fluid leakage | |
| CA1045095A (en) | Rotary vane compressor with vane extension means | |
| JPH11166494A (en) | Two-cylinder rotary compressor | |
| KR101684549B1 (en) | Rotary vacuum pump | |
| KR200236537Y1 (en) | Vane compressor | |
| KR101534877B1 (en) | a vane oil pump for a vehicle | |
| KR970070566A (en) | Vane pump | |
| JPH09287584A (en) | Rotary compressor | |
| KR101811695B1 (en) | Vane Typed Pump Having Rotating Cylinder | |
| JP2003286978A5 (en) | ||
| KR102087676B1 (en) | Minimum swash plate angle holding device of variable swash plate compressor | |
| KR102073108B1 (en) | Suctiion check valve for variable swash plate compressor and method of assembling thereof | |
| WO2016129334A1 (en) | Gas compressor | |
| KR100268259B1 (en) | Vane of rotary compressor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EEER | Examination request | ||
| MKLA | Lapsed |
Effective date: 20180426 |