Four-gear hydromechanical transmission

FIELD: engines and pumps.

SUBSTANCE: invention relates to a hydromechanical transmission incorporating a split mechanical and hydrostatic drives and is designed to be used in agricultural tractors. The hydromechanical four-gear infinitely-variable transmission incorporates planetary mechanism (32) including three planetary trains (34, 36, 38), four clutches (C1, C2, C3, C4) and brake (48) to throw in reverse. First hydrostatic assembly (20) is in mesh with planetary mechanism second crown gear (R2). In the First and Fourth gears, second hydrostatic assembly (18) is in mesh with carrier (28) thrown in by first clutch (C1). In the Second and Third gears, second hydrostatic assembly is thrown into mesh with sun gear (S2) of the planetary mechanism second train by second clutch (C2). In the First and Second gears third clutch (C3) meshes carrier (28) with output shaft (46). In the Third and Fourth gears, fourth clutch (C4) meshes sun gear (S2) of the second planetary train with output shaft (46). Third planetary train (38) incorporates brake (48) to throw in reverse. When brake (48) meshes to throw in reverse and both clutches, third and fourth, (C3, C4), are disengaged, third train sun gear (S3) and, hence, transmission output shaft (46) runs reverse.

EFFECT: infinitely-variable transmission with steady efficiency in operating conditions.

27 cl, 6 dwg

 

The technical field to which the invention relates.

The present invention relates to a hydromechanical transmission having both mechanical and hydrostatic branch, particularly to such a transmission, which is designed for use in an agricultural tractor.

The level of technology

The main problem with the transmission of power from the engine to the ground, whether it is an agricultural tractor or a road vehicle, is that for different working conditions need different gear ratios between the engine and the wheels or tracks. Traditionally this problem is solved by using discrete gear ratios. Such ratio can be selected manually, as it is produced in known transmissions with manual switch and controlled by the operator of a transmission shift speed by a servo. Gear ratio, can also be controlled via the transmission as it is in automatic transmissions, typically used in automobiles. However, there is a finite number of possible gear ratios, and these have gear ratios are not always optimal.

In this regard, preferably the use of continuously variable transmissions These transmissions are usually performed in the form of hydrostatic drives, which occur, for example, in self-propelled agricultural harvesting machines and tractors for lawns. Another solution is such an electric actuator, which is used in railway locomotives and, in a ground-moving equipment. Both solutions have drawbacks from the point of view of cost and efficiency.

Another solution of this problem - hydromechanical transmission. Hydromechanical are such transmission that combine mechanical transmission with a hydrostatic unit. Although mechanical transmission is usually more efficient and reliable than a purely hydrostatic transmission, they have drawbacks, not inherent in a continuously variable transmission, since they are more expensive than the hydrostatic transmission. In this way the main disadvantage of hydrostatic transmissions is that they are less efficient than mechanical. In addition, hydrostatic transmission usually require the use of bulky items such as large pumps and motors, which increases the amount of transmission. The main advantage of hydromechanical transmissions over hydrostatic drives is that part of the power is transmitted mechanically, allowing you to get bóa higher value of efficiency than in the case of purely hydrostatically the drives.

To satisfy existing constraints on volume, reduce cost, increase efficiency and provide stepless speed regulation, developed hydro-mechanical transmission that combine the best qualities of both types of transmissions. Hydromechanical transmission is usually performed with split flow input power so that the hydrostatic unit and a manual transmission are driven in parallel with a motor vehicle. To obtain the output hydromechanical power in numerous ranges of its size hydrostatic output power combine in a manual transmission with the mechanical power delivered from the engine separately. Each power range by changing the stroke length of the piston in the hydrostatic unit can steplessly change the speed and torque.

However, earlier attempts to use the hydromechanical transmission for agricultural tractors have drawbacks. In some known hydrostatic transmissions to perform switching between the ranges of low and high capacity is required to stop the vehicle. Among other some transmissions have a high degree of complexity of the design, while for other transmissions switching point PE is imow is in the range of the working area (corresponding to conduct field work), and the efficiency of the transmission in the switching point will be lower than in the interval between switching modes. In addition, many hydro-mechanical transmission to provide reversing require additional gear.

In the prior art there are three main types of hydro-mechanical circuits. The first type includes the type of joint entrance or separation torque. This circuit contains one hydrostatic unit, connected or are in toothed engagement with the input shaft of the transmission. Hydrostatic unit is usually performed with a variable volume. The other hydrostatic unit is connected or is in the grip of the planetary mechanism, providing separation torque. This unit is often a block with a fixed displacement. The second type of circuit with the joint entrance or separation speed. In the design of this type one hydrostatic unit connected to the output shaft of the transmission, and the other unit is connected or is in mesh with the planetary separation mechanism of torque. In practice, both the hydrostatic unit usually represent blocks of variable volume. The third type of circuit with four shafts or contour of the combined type. For this type of design Hydra is a static block is not connected either to the input shaft of the transmission, neither to the output shaft. Instead, both the hydrostatic unit is connected or are in engagement with the planetary mechanism, the separating torque. This can be used one or more than one planetary series.

In most hydromechanical transmissions use only one type hydromechanical circuit. Most often they use a circuit connected to the input shaft or the division of torque. These transmissions differ from each other by a number of ongoing operating modes and running gear, but hydromechanical circuit is made the same. You know, all three of these contours in a single transmission. Known transmissions of this type plays three modes, the first mode shape with the joint input, the second circuit of the combined type, and the third non-regenerative portion of the path with the joint input. The advantage of the transmission of this type is that both switching modes are synchronous, without breaking the flow of power. The main drawback of these transmissions is that for a given power level of the hydrostatic units are larger than in transmissions with a large number of transfers carried out by connecting the input shaft.

Thus, the merits of which t is a clear need for the creation of hydro-mechanical compact transmission, who can provide continuously adjustable within the range of realized it speeds without significant loss of efficiency in the operating range.

Disclosure of inventions

The purpose of this invention is to provide a hydromechanical transmission, ensuring the optimal functioning of an agricultural tractor.

Another objective of this invention is to provide a transmission housing, the length of such existing mechanical transmissions and allows you to easily place the transmission in the existing structures of the tractor with a minimum of modification for a particular tractor. Many used up to the present time of the transmission does not include in the combination of the mechanical transmission gear pair for reverse, but instead to switch between the direction of moving forward and backward contain separate gear pair that is located before or after the combined mechanical transmission. This design has a greater volume, and before switching the transfer made to move forward or backward, it may be necessary to stop the vehicle.

Described here hydromechanical transmission plays four modes of operation and has a planetary gear mechanism that includes three planetary the series along with four clutch and brake for reverse, that provides stepless speed regulation in the absence of additional gears for changing the direction of movement. The first hydrostatic unit is engaged with a crown gear of the second row planetary gear, designed for the separation of torque. In mode One and mode Four second hydrostatic unit is put in engagement with the planet carrier of the satellite through the first clutch and the gear pair. In modes Two and Three of the second hydrostatic unit via the second clutch and the second pair of gear wheels is put in engagement with the sun gear of the second row of the planetary mechanism that provides for the division of torque. In modes One and Two third clutch connects drove satellites with the output shaft. In modes Three and Four fourth clutch connects the sun gear of the second planetary series with the output shaft. There is also a brake for the implementation of the reverse (i.e. reverse)adjacent to the third planetary series. This planetary series contains six satellites, three of which are linked with a sun gear of the third row, but not in engagement with the crown gear, and the other three concatenated with a crown gear and not linked with a sun gear. Each satellite, which is carried the building with a sun gear, in addition, coupled with one of the satellites, which is coupled with a crown gear. Accordingly, when the brake to reverse included in the clutch, and the third and fourth clutches disengage, a sun gear of the third row and, therefore, the output shaft of the transmission are in reverse rotation.

The above and other objectives of this invention along with its advantages over the known analogues, which will become apparent from the following detailed description, are solved using a hydro-mechanical transmission, which includes: an input shaft adapted for connection with a source of rotational motion; an output shaft adapted for connection with a load; a hydrostatic transmission, containing the first hydrostatic unit, the second hydrostatic unit which is connected in fluid with the first hydrostatic unit; a mechanical transmission comprising a planetary mechanism, comprising: a first clutch, second clutch, the third clutch and the fourth clutch; the first element connected to the input shaft and driven in rotation; the second item in the drive coupling with the first hydrostatic unit; the third element selectively connected to the second hydrostatic unit by projapti clutch; the fourth element connected to the second hydrostatic unit via the second clutch and the fourth element is in drive connection with the second element, the fifth element, connected to the output shaft, and specified the fifth element selectively connected to the third element via a third clutch and is selectively connected to the fourth element via a fourth clutch; and a sixth element, selectively connected to the substrate using a brake, intended for realization of the reverse rotation, while the fifth element and the output shaft are driven in the implementation of reverse rotation.

Other objectives of the present invention are solved by using a hydro-mechanical transmission, comprising: an input shaft adapted for connection with a source of energy of rotational motion; an output shaft adapted for connection with a load, hydrostatic transmission, containing the first and second hydrostatic units, which are interconnected by fluid to one another; a mechanical transmission having a planetary gear with three planetary alignments, with a manual transmission has several input elements, of which one input element connected with the input shaft and, thereby, constantly in motion, and others who many input elements selectively attached to the second hydrostatic the block by means of two clutches, with a manual transmission combines the power coming from several input elements into a single total hydromechanical power output applied to the output shaft by using two clutches; and a brake for the implementation of the reverse gear are selectively connected to the planetary series mechanical transmission; due to this, the transmission plays four modes with the forward speed and two reverse mode with stepless speed in the interval between the highest speed reverse and the highest forward speed.

The following tasks of the present invention are solved by using a hydro-mechanical transmission, comprising: an input shaft adapted for connection with a source of energy of rotational motion; an output shaft adapted for connection with a load, the planetary mechanism, containing the first planetary line, the second planetary line and the third planetary series, with each planetary series has a sun gear and a few satellites, and each satellite of the first planetary series made integral with the respective satellites of the second planetary series so that they rotate together, the satellites each planetary series are mounted on a common drive rod, the second and third planetary alignments, except also, contain, each, caronno the gear; input shaft with the possibility of rotation of the drive connected to a sun gear of the first planetary series; drove selectively connected with the output shaft via a third clutch; a sun gear of the second planetary series selectively connected with the output shaft via a fourth clutch; the second hydrostatic unit selectively engaged with the planet carrier via a first clutch and gear pairs; and selectively engages with a sun gear of the second planetary series through the second clutch and the second gear pair; the first hydrostatic unit is engaged with a crown gear of the second planetary series, and the first hydrostatic unit communicates via a fluid with the second hydrostatic unit, while the first and second hydrostatic units are made with the possibility of changing the working volume so that the increase in displacement of the first hydrostatic unit reduces the working volume of the second hydrostatic unit and increases its speed, and Vice versa; a brake for the implementation of the reverse gear is selectively connected with a crown gear of the third planetary series; while in the output mode, One of the first and the third clutch are engaged, the working volume of the first hydrostatic unit is increased to the maximum, and the working volume of the second hydrostatic unit is reduced to zero; in the output mode, Two of the first coupler is removed from engagement of the second clutch is engaged, the working volume of the second hydrostatic unit increases as it changes in the opposite direction with respect to One mode, and the working volume of the first hydrostatic unit is reduced to until all elements of the planetary gear will not rotate with the same speed; in the output mode Three, the third clutch withdrawn from engagement, the fourth clutch is located in the clutch, the working volume of the first hydrostatic unit is increased to the maximum, and the working volume of the second hydrostatic unit is reduced to zero; in the output mode, Four second clutch removed from engagement of the first clutch is engaged, the working volume of the second hydrostatic unit is increased to the maximum as it changes in the opposite direction with respect to mode Three, and the working volume of the first hydrostatic unit is reduced to zero; and in the output modes One and Two for the implementation of the reverse brake for selectively reverse is engaged.

A number of further objectives of the present invention is solved by an agricultural tractor, comprising: a motor, when adnie wheel, hydromechanical transmission, the receiving drive from an engine and connected to drive wheels, with the possibility of driving rotation, with hydromechanical transmission includes: an input shaft adapted for connection with the engine, an output shaft adapted for connection with the drive wheels; a hydrostatic transmission, comprising: a first hydrostatic unit, the second hydrostatic unit which is connected in fluid with the first hydrostatic unit; a mechanical transmission having a planetary transmission comprising a first clutch, second clutch, the third clutch and the fourth clutch; the first element attached to the input shaft and thus driven in rotation; the second item in the drive coupling with the first hydrostatic unit; the third element selectively connected with the second hydrostatic unit through a first clutch; a fourth element, selectively connectable with the second hydrostatic unit via the second clutch; a fourth element, which is in drive connection with the second element, the fifth element, selectively connected to the third element via a third clutch and is selectively connected to the fourth element through the first mu is you clutch; and the sixth element selectively connected to the substrate using a brake to reverse, with the implementation of the reverse (reverse) are given in the fifth rotation element and the output shaft; the transmission reproduces the four speeds forward and two reverse speed with stepless speed between the speed limit and reverse limit forward speed.

As information for professionals in the field of technology is closely associated with the present invention, herein disclosed one preferred embodiment of the invention, which shows the best currently considered a practical implementation of the invention, with reference to the accompanying drawings, forming part of this specification. Below is described a typical example of the embodiment. Show all the various forms and modifications in which might be embodied, the invention, in the task description is not included. As such, presents and described embodiment of the invention is illustrative, and as will be clear to experts, it can be modified in many ways within the scope and essence of the invention, while the present invention is characterized by the attached claims and not described in detail the s.

Brief description of drawings

For a full understanding of the objectives of the present invention, as well as hardware and circuit design used according to the invention, it is necessary to refer to the following detailed description and accompanying drawings.

Figure 1 is a kinematic diagram of the hydro-mechanical transmission in accordance with the present invention.

Figure 2 is a kinematic diagram of a hydromechanical transmission corresponding to the present invention operating in mode One.

Figure 3 is a kinematic diagram of a hydromechanical transmission corresponding to the present invention operating in mode Two.

4 is a kinematic diagram of a hydromechanical transmission corresponding to the present invention operating in mode Three.

5 is a kinematic diagram of a hydromechanical transmission corresponding to the present invention operating in mode Four.

6 is a chart showing the relationship between displacement of the hydrostatic unit and the speed of the earth.

The implementation of the invention

Hydromechanical transmission according to the present invention is shown schematically in figure 1 and indicated in General position 10. The transmission 10 has an input shaft 12 adapted for connection with a motor (not shown) or other source is the infrared energy of rotational motion and obtain from him drive. The transmission has a pair of hydrostatic units 18 and 20. These units are hydraulically connected by means of piping (not shown) with the formation of a hydrostatic transmission. Both units 18 and 20 are devices with variable volume.

The transmission 10 includes a combined mechanical transmission 30 containing the planetary gear mechanism 32. The planetary mechanism 32 includes three planetary series 34, 36 and 38. Planetary alignments have common carrier 28, which moves the satellites P1 and P2 planetary gear sets 34 and 36, respectively. Drove 28, also moves the satellites P3 and P4 planetary series 38 reverse. Satellites P1 and P2 are made in one piece and thus rotate together. This satellite P2 is connected with a crown gear R2. Crown gear R2 is made in one piece with the gear 40. This gear 40 is driven into rotation of the drive gear 42 mounted on the output shaft 44 of the hydrostatic unit 20. In the crown gear R2 is the input element for the perception of the hydrostatic power.

Input shaft 12 of the transmission, in addition, causes the rotation of the sun gear S1 of the first planetary number 34 with the gear 14 and the gear 16 and shaft 17, thereby the sun gear S1 is an input element for the perception of mechanical power. The sun gear S1 nah who is in the grip satellite P1. Planetary line 36 includes a sun gear S2, which is in mesh with satellite P2.

Clutch C3 and C4 selectively connects the elements of the planetary mechanism output shaft 46 of the mechanical transmission. Clutch C3 can engage to ensure the connection carrier 28 with the output shaft 46 in the range of low speeds forward. Clutch C4 may engage to connect the sun gear S2 to the output shaft 46 in the interval of high speed forward movement.

The output 22 of the hydrostatic unit 18 is selectively connected to the cage 28 through the clutch C1 and the gear 23 and 24. In addition, the output 22 is selectively connected to the shaft 25 and the sun gear S2 via the clutch C2 and the gear 26 and 27.

The output shaft 46 is attached to the sun gear S3. Crown gear R3 is selectively connected to the base through the brake 48 for reverse. This leads to the stop of rotation of the crown gear R3 and the rotation of the sun gear S3 in the opposite direction at speeds reverse. When the brake 48 to reverse is actuated and the clutch C3 and C4 are derived from the gearing, a sun gear S3 causes the rotation of the output shaft 46.

The output shaft 46 of the mechanical transmission is made in one piece with the gear 50, which, in turn, is included in azepine with the gear 52, installed on the offset (relative to the shaft 46) shaft 54. Offset shaft 54 is attached to the differential drive shaft (not shown) of a tractor, designed to connect hydro-mechanical transmission 10 with the load.

The transmission 10 operates in four modes. Each mode implements a separate path (transmission power) through the mechanical transmission 30 to the output shaft 46, with the result that each band get their gear ratio.

The operation of the transmission mode One

In the operating mode of One of the clutches C1 and C3 are engaged, as shown in figure 2. At zero speed of rotation of the output shaft of the hydrostatic unit 18 is in the position of maximum displacement and because it is connected to the output via the clutch C1 and C3, its speed is zero. At zero speed of the output shaft of the hydrostatic unit 20 has a relatively high speed. To bring the output shaft of the transmission of the rotation of the displacement of hydrostatic unit 20 increases, causing it to pump fluid in hydrostatic unit 18, forcing thereby the hydraulic unit 18 and the output shaft to rotate. When the working volume of the hydrostatic unit 20 reaches its maximum value, the unit 20 remains at the maximum working volume, at the same time, the working volume of the m hydrostatic unit 18 is reduced. When reducing the displacement of hydrostatic unit 18 to a zero fluid flow to the hydrostatic unit 20 from him is blocked, which leads to the stop of rotation of the hydrostatic unit 20 and the crown gear R2. When the hydrostatic unit 20 is at zero speed, and the hydrostatic unit 18 is at zero working volume, hydrostatic power is equal to zero and all power is transmitted mechanically. In this case, for switching on the operating mode Two clutch C1 is removed from engagement, and the clutch C2 is introduced into the mesh. Since the hydrostatic unit 18 is at zero working volume, the nominal torque is equal to zero. Gearing with clutch C1 and C3 is chosen so that when the switching mode One to mode Two speed clutch elements relative to the clutch C2 is zero. Because of the need to ensure synchronization conditions and zero torque the clutches C1 and C2 can be any coupling with the usual friction disks or mechanisms of the switching Cam of the type that is usually used for manual switching of transmissions. In One mode reverse (back) is done by entering the brake 48 to reverse engage or disengage the output clutch C3 from the mesh. This allows the sun gear 53 and, hence, output is mu shaft of the transmission to make a reverse rotation.

Mode Two

As shown in figure 3, the clutch C2 and C3 are engaged. When the minimum speed of rotation of the output shaft in mode Two hydrostatic unit 18 has zero displacement and high speed, while the hydrostatic unit 20 has a maximum working volume and zero speed. To increase the output speed of displacement of hydrostatic unit 18 increases as it changes in the opposite direction with respect to mode One. This decreases the rotation speed of the hydrostatic unit 18 and to increase the rotation speed of the hydrostatic unit 20. After working volume of the hydrostatic unit 18 reaches the maximum it supports a maximum, at the same time, the working volume of the hydrostatic unit 20 is reduced. In this mode, the working volume of the hydrostatic unit 20 decreases as long as the speed of the crown gear R2 will not be the same as the speed of the sun gear S1. When switching from mode Two to mode One displacement hydrostatic unit 20 will be approximately 60-65% of the displacement of hydrostatic unit 18, but, generally speaking, this value depends on the specific gear ratio. At this time, the clutch C4 may be engaged, and the clutch C3 can be derived the C gear. Since all the elements of the planetary mechanism, the separating torque, rotate at the same speed, switching from mode One to mode Three will also be synchronous, because all the elements of the clutch C4 clutch are rotating at the same speed. However, these clutch will transmit torque, therefore, the clutch C4 must be brought into engagement before C3 is removed from the mesh, otherwise the flow of power is interrupted. In mode Two for the implementation of the reverse (reverse) brake 48 reverse is engaged, and the clutch C3 is shown out of engagement that allows the sun gear S3, and therefore the output shaft of the transmission to make a reverse rotation.

Mode Three

As shown in figure 4, the clutch C2 and C4 are in the position of the clutch. When the minimum speed of rotation of the output shaft in mode Three working volume and speed of both hydrostatic units 18 and 20 are the same as in mode Two at the maximum output speed. To increase the output speed in mode Three displacement hydrostatic unit 20 is increased to maximum. Then, maintaining the hydrostatic unit 20 with a maximum working volume working volume of the hydrostatic unit 18 is reduced to zero, further increasing output speed. At this time, the hydrostatic unit 18, the work is the second volume of which is equal to zero, blocks the fluid flow as a hydrostatic unit 20, and from this block, stopping, thereby, rotation of the hydrostatic unit 20. To switch from mode Three mode Four clutch C2 is output gear and the clutch C1 is introduced into the mesh. Torque and speed of these clutches are the same as when switching from mode One to mode Two. In addition, all power is transmitted mechanically, as and when switching from mode One to mode Two. In mode Three, reverse (reverse) is not supported.

Mode Four

As shown in figure 5, the clutches C1 and C4 are in the position of the clutch. When the minimum speed of rotation of the output shaft in mode Four working volume and speed of both hydrostatic units 18 and 20 are the same as in mode Three at the maximum output speed. To increase the output speed in mode Four displacement hydrostatic unit 18 increases to a maximum when it is modified in the opposite direction with respect to the modes Two and Three. While hydrostatic unit 18 is supported at a maximum working volume working volume of the hydrostatic unit 20 is reduced to zero. At this time, the speed of the hydrostatic unit 18 is zero, hydrostatic power is equal to zero, and all power is transmitted mechanically. Reverse the mode Four is not provided.

6 illustrates the relative displacement hydrostatic units 18 and 20, depending on the speed of movement on the ground. Line, designated as H1, shows the percentage displacement of hydrostatic unit 20, while the line H2 shows the percentage displacement of hydrostatic unit 18. The point of switching from mode One to mode Two marked position SP1. The point of switching from mode Two to mode Three designated position SP2. The switching point with mode Three mode Four designated position SP3. Graphic dependence figure 6 is shown to illustrate the magnitude of the displacement hydrostatic units depending on the speed of movement along the ground in one preferred embodiment of the present invention. Specialists in the art it is clear that the values of speed of movement on the earth depend on a number of variables such as the size of the gears, tire size and the number of engine revolutions per minute.

The above hydromechanical transmission is different from the transmission famous counterparts, the fact that it has four modes of a forward stroke and two reverse mode and uses two of the three known types of hydro-mechanical circuits. When driving forward and in reverse mode One involved the contour with the merged output. In the case of forward motion and p is and the implementation of the reverse mode Two is implemented, the combined contour type. Moving forward in mode Three is implemented by a circuit with a combined entrance and moving forward in mode Four - combined type circuit. In the transmission plays three output gear ratios for forward movement, in which the hydrostatic power is equal to zero. This ratio corresponds to the switching point from mode One to mode Two, the switching point mode Three mode Four and maximum ratio transmission. Since near of the specified operating points hydrostatic power is small, near these operating points to achieve high transmission efficiency. In addition, in the above-described transmission is used only four clutch and one brake for the four operating modes forward and two reverse modes. For comparison, previously known multi-circuit transmission using at least five of the clutch and one brake to implement three working modes forward and three reverse mode. Accordingly disclosed in the present description, the transmission has an advantage from the standpoint of cost and simplicity of construction. In addition, due to the use of these four modes of operation of the proposed transmission solves the problem of large dimensions hydrostatic unit. This transmission mo is no use hydrostatic blocks of the same size, as in the case of transmissions is much smaller capacity. In addition, this transmission solves the problem of low efficiency in the switching point in the working range. Although in the disclosed here, the transmission mode switching is performed specifically at a speed of about 9 km/h, which is commonly used operating speed, all power is transmitted mechanically and, therefore, the switching point is characterized by a slight decrease in efficiency or no loss of efficiency. The decrease in efficiency occurs after switching from mode Two and mode Three, but this occurs at a speed of approximately 20 km/h, which is the speed, as a rule, not used in field work or transportation, so that this influence is not significant. At this speed hydrostatic power is less than 50%, so the efficiency remains relatively high.

As can be seen from the above, the objectives of this invention are solved by using the transmission scheme described above. While in accordance with patent law here shown and disclosed in detail only the best modes and preferred examples of embodiment of the invention, this does not mean that they are exhaustive or given to limit the invention described a specific form of embodiment. In light of the above possible is obvious the derivative modifications or options. The above embodiment was chosen and described in order to best illustrate the principles of this invention and illustrate its implementation in practice, to any of the medium-specialists in the art to use the invention in various embodiments and modifications which are appropriate for the specific intended use. All such modifications and variations consistent with the scope of the present invention defined by the attached claims in their interpretation of the breadth with which they duly and lawfully provide the right to the patent.

1. Hydromechanical transmission comprising an input shaft (12)adapted for connection with a source of energy of rotational motion; an output shaft (54)adapted for connection with a load; a hydrostatic transmission, containing the first hydrostatic unit (20) and the second hydrostatic unit (18)which is connected in fluid with the first hydrostatic unit (20); mechanical transmission (30), containing a planetary gear mechanism (32)includes a first clutch (C1) clutch, a second clutch (C2) clutch, the third clutch (C3) and fourth clutch clutch (C4) clutch; the first element (S1)connected to the input shaft (12) and driven in rotation; the second element (R2)in the drive stepl the Institute with the first hydrostatic unit (20); the third element (28)is selectively connected to the second hydrostatic unit (18) via the first clutch (C1) clutch; the fourth element (S2)is selectively connected to the second hydrostatic unit (18) via the second clutch (C2) clutch, the fourth element (S2), connected to the drive capability of the second element (R2); the fifth element (S3)connected with the output shaft (46), while the fifth element (S3) is selectively connected with the third element (28) via the third clutch (C3) clutch and selectively connected to the fourth element (S2) via the fourth clutch (C4) clutch; and the sixth element (R3)is selectively connected to ground through the brake (48) to reverse, while the fifth element (S3) and output shaft (46) are rotated in the implementation of the reverse.

2. Hydromechanical transmission according to claim 1, in which the planetary mechanism (32) has three planetary series(34, 36, 38).

3. Hydromechanical transmission according to claim 2, in which the first and second planetary alignments (34, 36) contain the first and second satellites (P1, P2), respectively, which are attached to one another for joint rotation.

4. Hydromechanical transmission according to claim 2, in which three planetary series (34, 36, 38) have a common carrier (28).

5. Hydromechanical transmission according to claim 4, in which the carrier (28) is specified by the third element, and bertele connected to the second hydrostatic unit (18) via clutch (C1) clutch.

6. Hydromechanical transmission according to claim 4, in which three planetary series (34, 36, 38) contain the first satellites (P1)which engages with the first sun gear (S1), second satellites (P2)which engages with the second sun gear (S2), and the third crown gear (R2), and in which the first satellites (P1) is attached to the second satellite (P2), whereby they rotate at the same speed.

7. Hydrodynamic transmission according to claim 6, in which the first sun gear (S1) is specified by the first element, and the first crown gear (R1) is specified by the second element.

8. Hydrodynamic transmission according to claim 6, in which the third sun gear (S3) is specified as the fifth element and is fixed to the output shaft (46).

9. Hydrodynamic transmission of claim 8, in which the second crown gear (R3) is specified the sixth element.

10. Hydrodynamic transmission comprising: an input shaft (12)adapted for connection with a source of energy of rotational motion; an output shaft (54)adapted for connection with a load; a hydrostatic transmission, containing the first and second hydrostatic units (20, 18), connected for fluid to one another; mechanical transmission (30), containing a planetary gear (32) with three planetary alignments (34, 36, 38), if it is a manual transmission (30) has multiple input elements (17, 28, S2), of which one input element (17) is connected with an input shaft (12), which is continuously in rotation, and other input elements (28, S2) is selectively connected with the second hydrostatic unit (18) via clutch (C1, C2) clutch and a manual transmission (30) combines the power supplied from a large number of input elements (17, 28, S2), using two couplings (C3, C4) coupling, in a single output (54) hydromechanical power connected with the output shaft (46); and brake (48) for the implementation of the reverse, selectively connectable with the planet close (38) mechanical transmission (30); as a result, the transmission (10) has a four speed forward and two speed reverse with stepless speed in the interval between the maximum speed reverse and maximum speed of forward movement.

11. Hydromechanical transmission of claim 10, in which the first and second planetary alignments (34, 36) contain the first and second satellites (P1, P2), respectively, which are attached to one another for joint rotation.

12. Hydromechanical transmission of claim 10, in which three planetary series (34, 36, 38) have a common carrier (28).

13. Hydromechanical transmission according to item 12, in which the carrier (28) is specified by the third element selectively connected to in Oromo hydrostatic unit (18) via clutch (C1) clutch.

14. Hydromechanical transmission according to item 12, in which three planetary series (34, 36, 38) contain the first satellites (P1)which engages with the first sun gear (S1), second satellites (P2)which engages with the second sun gear (S2), and the third crown gear (R2), and in which the first satellites (P1) is attached to the second satellite (P2), whereby they rotate at the same speed.

15. Hydromechanical transmission according to 14, in which the second sun gear (S2) is one of several inputs selectively connected to the second hydrostatic unit (18).

16. Hydromechanical transmission according to 14, in which the third sun gear (S3) of the third planetary series (38) attached to the output shaft (46).

17. Hydromechanical transmission according to clause 16, in which the second ring gear (R3) of the third planetary series (38) selectively connected to the ground with brakes (48) for the implementation of the reverse.

18. Hydrodynamic transmission comprising: an input shaft (12)adapted for connection with a source of energy of rotational motion; an output shaft (54)adapted for connection with a load; a planetary mechanism (32)includes a first planetary series (34), the second planetary line (36) and the third planetary number (38), each of the planetary series (4, 36, 38) includes a sun gear (S1, S2, S3) and multiple satellites (P1, P2, P3, P4), and each satellite (P1) of the first planetary series (34) made at the same time with the satellite (P2) of the second planetary series (36) so that they rotate together, the satellites (P1, P2, P3, P4) of each planetary series (34, 36, 38) are mounted on a common drive rod (28), and the second and third planetary alignments (36, 38) each, in addition, contain the crown gear (R2, R3), and the input shaft (12) is connected with a sun gear (S1) of the first planetary series (34), with the possibility of the drive carrier (28) is selectively connected with the output shaft (46, 54) via the third clutch (C3) clutch; a sun gear (S2) of the second planetary series (36) selectively connected with the output shaft (46, 54) via the fourth clutch (C4) clutch; the second hydrostatic unit (18) selectively engages with the planet carrier (28) via the first clutch C1 clutch and the gear pair (23, 24) and selectively engages with a sun gear (S2) of the second planetary series (36) via the second clutch (C2) clutch and the second gear pair (26, 27); the first hydrostatic unit (20) is engaged with a crown gear (R2) of the second planetary series (36), and the first and second hydrostatic units (20, 18) is configured to selectively modify the working volume so that Uwe is ikenie displacement of the first hydrostatic unit (18) reduces the working volume of the second hydrostatic unit and increases its speed, and Vice versa; and a brake (48) for the implementation of the reverse gear is selectively connected with a crown gear (R3) of the third planetary series (38), while in the output mode, One of the first and the third clutches (C1, C3) clutch are in engagement, the working volume of the first hydrostatic unit (18) is increased to the maximum, and the working volume of the second hydrostatic unit (20) is reduced to zero; in the output mode, Two of the first clutch (C1) derived from engagement of the second clutch (C2) is engaged, the working volume of the second hydrostatic unit (18) increases as it changes in the opposite direction with respect to One mode, and the working volume of the first hydrostatic unit (20) is reduced to until all of the elements of the planetary mechanism (32) will not rotate with the same speed; in the output mode Three, the third clutch (C3) clutch removed from engagement of the fourth clutch (C4) is in the clutch, the working volume of the first hydrostatic unit (20) is increased to the maximum, and the working volume of the second hydrostatic unit (18) is reduced to zero; in the output mode, Four second clutch (C2) clutch removed from engagement of the first clutch C1 is engaged, the working volume of the second hydrostatic unit (18) is increased to the maximum as it changes in the opposite directed and in relation to mode Three, and the working volume of the first hydrostatic unit (20) is reduced to zero; and for reversing the output modes One and Two brake (48) for selectively reverse is engaged.

19. Agricultural tractor, comprising: a motor; a drive wheel; hydro-mechanical transmission (10)actuated by the engine and connected to drive wheels, comprising: an input shaft (12)adapted for connection with the engine; an output shaft (54)adapted for connection with the drive wheels; a hydrostatic transmission, containing the first hydrostatic unit (20) and the second hydrostatic unit (18)which is connected in fluid with the first hydrostatic unit (20); mechanical transmission (30), containing a planetary gear mechanism (32), comprising: the first clutch C1 clutch, a second clutch (C2) clutch, the third clutch (C3) clutch and the fourth clutch (C4) clutch; the first element (S1)connected to the input shaft (12) and driven in rotation; the second element (R2)in the drive coupling with the first hydrostatic unit (20); the third element (28) is selectively connected to the second hydrostatic unit (18) via the first clutch (C1) clutch; the fourth element (S2)is selectively connected to the second hydrostatic unit (18) using the second m is fty (C2) clutch the fourth element (S2), connected to the drive capability of the second element (R2); the fifth element (S3)connected with the output shaft (46), while the fifth element (S3) is selectively connected with the third element (28) via the third clutch (C3) clutch, selectively connects the fourth element (S2) via the fourth clutch (C4) clutch; and the sixth element (R3)is selectively connected to ground through the brake (48) to reverse, while the fifth element (S3) and the output the shaft (46) are rotated in the implementation of the reverse; and the result of the execution of the transmission (10) has four modes speeds forward and two reverse speed with stepless speed in the interval between the maximum speed reverse and maximum speed of forward movement.

20. Agricultural tractor according to claim 19, in which the planetary gear mechanism (32) has three planetary series(34, 36, 38).

21. Agricultural tractor according to claim 20, in which the first and second planetary alignments (34, 36) contain the first and second satellites (P1, P2), respectively, which are attached to one another for joint rotation.

22. Agricultural tractor according to claim 20, in which the three planetary series (34, 36, 38) have a common carrier (28).

23. Agricultural tractor according to article 22, in which the carrier (28) is specified third e the COP, selectively connected to the second hydrostatic unit (18) via clutch (C1) clutch.

24. Agricultural tractor according to article 22, in which the three planetary series (34, 36, 38) contain the first satellites (P1)which engages with the first sun gear (S1), second satellites (P2)which engages with the second sun gear (S2), and the third crown gear (R2), and in which the first satellites (P1) is attached to the second satellite (P2), whereby they rotate at the same speed.

25. Agricultural tractor according to paragraph 24, in which the first sun gear (S1) is specified by the first element, and the first crown gear (R1) is specified by the second element.

26. Agricultural tractor according to paragraph 24, in which the third sun gear (S3) is specified as the fifth element and is fixed to the output shaft (46).

27. Agricultural tractor on p, in which the second crown gear (R3) is specified the sixth element.



 

Same patents:

Gear variator // 2325570

FIELD: engines and pumps.

SUBSTANCE: invention refers to devices for stepless converters of torque and rotary motion. A gear variator contains two differential mechanisms (1, 2), two reducers (3, 4) with different ratios. One of the shafts of each reducer is connected to a hydro pump (11) equipped with an adjustable valve. Two differential mechanisms and two reducers are arranged so that input shafts of the reducers are at the same time half axes of the first differential mechanism, while output shafts of reducers are half axes of the second differential mechanism. The differential allows distribution of rotation between half axes within range from zero to a speed of a drive shaft on one of the half axes which corresponds to interval from the speed of the drive shaft to zero on the other half axis. A rotation speed of the variator driven shaft can be adjusted by means of adjustable valves through which liquid is pumped by gear oil pumps driven with specified shafts of the mechanism.

EFFECT: variator allows to change value of torque within any given range.

2 dwg

FIELD: mechanical engineering.

SUBSTANCE: variable-speed drive comprises two differential stages connected in series. The differential sage whose shaft is connected with the engine is the input shaft of the variable-speed drive and is made of a differential mechanism. The second differential stage is a hydraulic differential converter provided with two planet rows defined by the kinematical links of multi-gearing hydraulic pump and hydraulic motor provided with different gear ratios . The axles of the satellites of the first and second differential stages are mounted inside the housing . The housing is set in bearings inside the crankcase of the variable-speed drive and represents a carrier for both of the differential stages. The carrier is provided with the free running clutch.

EFFECT: enhanced efficiency.

2 dwg

FIELD: mechanical engineering.

SUBSTANCE: infinitely variable transmission comprises power differential (1), synchronizing differential (2), two self-braking mechanisms (3) and (4), and two controllers. The input of power differential (1) is connected with the drive and input of synchronizing differential (2). Central wheels (17) and (18) of the power differential are connected with driven links (15) and (16) of self-braking mechanisms (3) and (4). Driving links (13) and (14) of self-braking mechanisms are connected with central wheels (19) and (20) of the synchronizing differential and controllers. Driven shaft (26) is connected with one of the central wheels of power differential (1).

EFFECT: expanded functional capabilities.

1 dwg

FIELD: mechanical engineering and machine-tool building.

SUBSTANCE: invention can be used in vehicles and machine tools, different machines and mechanisms. Proposed continuously-variable transmission contains drive and output shafts and case accommodating drive and drive and driven constant-mesh gears, differential with coaxial gears mechanically engaging through planet pinions and provided with coaxial axle-shafts, and gear ratio changer including axial-plunger pump with inclined plate with rotary working member, pressure line and suction line connected with reservoir filled with working liquid. Adjustable bypass restrictor is installed in pressure line of pump. Output of restrictor is connected with said reservoir by drain line. Rotary working member of pump is made in form of block of working cylinders accommodating plungers, each being mechanically coupled with inclined plate. Differential is arranged inside working cylinder block of axial-plunger pump with coaxial arrangement of drive and driven gears and said block, and it has at least one pair of planet pinions installed for rotation in cylinder block of axial-plunger pump. Constant-mesh drive gear is connected with drive shaft, and constant-mesh driven gear is connected with drive gear of differential. Invention is aimed at enlarging functional capabilities of transmission owing to provision of limitation of speed of rotation and braking of output shaft, interruption of torque on shaft and control of delivery of pump included into gear ratio changer of transmission and increase of service life and provision of uniform rotation of output shaft and increase of efficiency of transmission.

EFFECT: enlarged operating capabilities, increased efficiency of transmission.

22 cl, 4 dwg

FIELD: transport engineering.

SUBSTANCE: invention can be used as gearbox in vehicles or as actuator in tank armament stabilizers. Proposed stepless transmission contains power differential 1, comparing differential 30, regulating differential 2, two self-braking mechanisms 3, 4 operating in release mode, two regulators, and mechanism 36 for equalizing speeds of rotation of central gears of regulating differential. Input of power differential 1 is connected with drive and with input of regulating differential 2. Central gears 17, 18 of power differential are rigidly connected with driven members 15, 16 of self-braking mechanisms and are connected with central gears of comparing differential 30 to provide rotation of the latter in opposite directions. Driving members 13, 14 of self-braking mechanisms are connected with central gears of regulating differential by mechanism 36 equalizing speeds of rotation and are rigidly connected with regulators.

EFFECT: enlarged range of change of gear ratio, improved dynamic characteristics of vehicle, its reliability and multipurposeness.

1 dwg

FIELD: mechanical engineering.

SUBSTANCE: positive-displacement hydraulic-mechanical transmission comprises input shaft (1), output shaft (2), two interconnected reversible controlled hydraulic motors (3) and (4), four-link differential (5), and pumping devices (12), (13), (14), and (15). Satellites (7) and (8) of differential (5) are made in pairs and engage each other. Satellite (8) is wide and interposed between the large solar gear (10) and central wheel (11) with the inner engagement. Satellite (7) is narrow and engages small solar gear (9). Two switching devices (14) and (15) connect the shaft of hydraulic motor (4) with input shaft (1) of the transmission and central wheel (11) with the inner engagement. Two switching devices (12) and (13) connect the shaft of hydraulic motor (3) with output shaft (2) of the transmission and small solar gear (9) of the differential.

EFFECT: reduced mass and sizes and enhanced efficiency.

1 dwg, 1 tbl

FIELD: mechanical engineering.

SUBSTANCE: infinitely variable reduction gear comprises input shaft connected with the driving electric motor and output shaft provided with a longitudinal opening connected with the controllable throttle through the coupling. The throttle is connected with the rotatable housing which receives the hydraulic braking device mounted inside the vessel. The hydraulic braking device is made of worm gearing whose worm wheel is connected with the output shaft. The worm wheel is coupled with two worm shafts arranged from both sides of the worm wheel. The axle of each worm shafts is connected with the gearing pump whose intake is connected with the space of the vessel and outlet is connected with the opening in the output shaft.

EFFECT: enhanced reliability and simplified structure.

1 dwg

FIELD: transport engineering.

SUBSTANCE: invention relates to crawler tractors and it can be used in their full-flow hydrostatic transmissions. Said transmission contains dividing reduction unit 2, two parallel final hydrostatic drives with pumps 3, 4 and hydraulic motors 5, 6, track reduction units 17, 18 and two planetary mechanisms. Planetary mechanisms are installed between hydraulic motors 17, 18 and track reduction units 17, 18. Sun gears 9, 10 of planetary mechanisms are connected with each hydraulic motor by two similar gear trains 7, 9. Carriers 11, 12 of each planetary mechanism are connected with epicyclic wheels 14, 13 of other planetary mechanism and with track reduction units 17, 18. invention improves maneuverability of tractor, provides economic recuperation of brake power from trailing side to leading side at turning of tractor, reduced power load on engine at turning, reduced power losses in hydrostatic drives of transmission of tractor with possibility of use of hydrostatic drives of lower installed power.

EFFECT: improved service characteristics of tractor.

1 dwg

The invention relates to a transport engineering

The invention relates to mechanical engineering and can be used in hydraulic drive control for continuously variable transmission

FIELD: transport engineering.

SUBSTANCE: invention relates to crawler tractors and it can be used in their full-flow hydrostatic transmissions. Said transmission contains dividing reduction unit 2, two parallel final hydrostatic drives with pumps 3, 4 and hydraulic motors 5, 6, track reduction units 17, 18 and two planetary mechanisms. Planetary mechanisms are installed between hydraulic motors 17, 18 and track reduction units 17, 18. Sun gears 9, 10 of planetary mechanisms are connected with each hydraulic motor by two similar gear trains 7, 9. Carriers 11, 12 of each planetary mechanism are connected with epicyclic wheels 14, 13 of other planetary mechanism and with track reduction units 17, 18. invention improves maneuverability of tractor, provides economic recuperation of brake power from trailing side to leading side at turning of tractor, reduced power load on engine at turning, reduced power losses in hydrostatic drives of transmission of tractor with possibility of use of hydrostatic drives of lower installed power.

EFFECT: improved service characteristics of tractor.

1 dwg

FIELD: mechanical engineering.

SUBSTANCE: infinitely variable reduction gear comprises input shaft connected with the driving electric motor and output shaft provided with a longitudinal opening connected with the controllable throttle through the coupling. The throttle is connected with the rotatable housing which receives the hydraulic braking device mounted inside the vessel. The hydraulic braking device is made of worm gearing whose worm wheel is connected with the output shaft. The worm wheel is coupled with two worm shafts arranged from both sides of the worm wheel. The axle of each worm shafts is connected with the gearing pump whose intake is connected with the space of the vessel and outlet is connected with the opening in the output shaft.

EFFECT: enhanced reliability and simplified structure.

1 dwg

FIELD: mechanical engineering.

SUBSTANCE: positive-displacement hydraulic-mechanical transmission comprises input shaft (1), output shaft (2), two interconnected reversible controlled hydraulic motors (3) and (4), four-link differential (5), and pumping devices (12), (13), (14), and (15). Satellites (7) and (8) of differential (5) are made in pairs and engage each other. Satellite (8) is wide and interposed between the large solar gear (10) and central wheel (11) with the inner engagement. Satellite (7) is narrow and engages small solar gear (9). Two switching devices (14) and (15) connect the shaft of hydraulic motor (4) with input shaft (1) of the transmission and central wheel (11) with the inner engagement. Two switching devices (12) and (13) connect the shaft of hydraulic motor (3) with output shaft (2) of the transmission and small solar gear (9) of the differential.

EFFECT: reduced mass and sizes and enhanced efficiency.

1 dwg, 1 tbl

FIELD: transport engineering.

SUBSTANCE: invention can be used as gearbox in vehicles or as actuator in tank armament stabilizers. Proposed stepless transmission contains power differential 1, comparing differential 30, regulating differential 2, two self-braking mechanisms 3, 4 operating in release mode, two regulators, and mechanism 36 for equalizing speeds of rotation of central gears of regulating differential. Input of power differential 1 is connected with drive and with input of regulating differential 2. Central gears 17, 18 of power differential are rigidly connected with driven members 15, 16 of self-braking mechanisms and are connected with central gears of comparing differential 30 to provide rotation of the latter in opposite directions. Driving members 13, 14 of self-braking mechanisms are connected with central gears of regulating differential by mechanism 36 equalizing speeds of rotation and are rigidly connected with regulators.

EFFECT: enlarged range of change of gear ratio, improved dynamic characteristics of vehicle, its reliability and multipurposeness.

1 dwg

FIELD: mechanical engineering and machine-tool building.

SUBSTANCE: invention can be used in vehicles and machine tools, different machines and mechanisms. Proposed continuously-variable transmission contains drive and output shafts and case accommodating drive and drive and driven constant-mesh gears, differential with coaxial gears mechanically engaging through planet pinions and provided with coaxial axle-shafts, and gear ratio changer including axial-plunger pump with inclined plate with rotary working member, pressure line and suction line connected with reservoir filled with working liquid. Adjustable bypass restrictor is installed in pressure line of pump. Output of restrictor is connected with said reservoir by drain line. Rotary working member of pump is made in form of block of working cylinders accommodating plungers, each being mechanically coupled with inclined plate. Differential is arranged inside working cylinder block of axial-plunger pump with coaxial arrangement of drive and driven gears and said block, and it has at least one pair of planet pinions installed for rotation in cylinder block of axial-plunger pump. Constant-mesh drive gear is connected with drive shaft, and constant-mesh driven gear is connected with drive gear of differential. Invention is aimed at enlarging functional capabilities of transmission owing to provision of limitation of speed of rotation and braking of output shaft, interruption of torque on shaft and control of delivery of pump included into gear ratio changer of transmission and increase of service life and provision of uniform rotation of output shaft and increase of efficiency of transmission.

EFFECT: enlarged operating capabilities, increased efficiency of transmission.

22 cl, 4 dwg

FIELD: mechanical engineering.

SUBSTANCE: infinitely variable transmission comprises power differential (1), synchronizing differential (2), two self-braking mechanisms (3) and (4), and two controllers. The input of power differential (1) is connected with the drive and input of synchronizing differential (2). Central wheels (17) and (18) of the power differential are connected with driven links (15) and (16) of self-braking mechanisms (3) and (4). Driving links (13) and (14) of self-braking mechanisms are connected with central wheels (19) and (20) of the synchronizing differential and controllers. Driven shaft (26) is connected with one of the central wheels of power differential (1).

EFFECT: expanded functional capabilities.

1 dwg

FIELD: mechanical engineering.

SUBSTANCE: variable-speed drive comprises two differential stages connected in series. The differential sage whose shaft is connected with the engine is the input shaft of the variable-speed drive and is made of a differential mechanism. The second differential stage is a hydraulic differential converter provided with two planet rows defined by the kinematical links of multi-gearing hydraulic pump and hydraulic motor provided with different gear ratios . The axles of the satellites of the first and second differential stages are mounted inside the housing . The housing is set in bearings inside the crankcase of the variable-speed drive and represents a carrier for both of the differential stages. The carrier is provided with the free running clutch.

EFFECT: enhanced efficiency.

2 dwg

Gear variator // 2325570

FIELD: engines and pumps.

SUBSTANCE: invention refers to devices for stepless converters of torque and rotary motion. A gear variator contains two differential mechanisms (1, 2), two reducers (3, 4) with different ratios. One of the shafts of each reducer is connected to a hydro pump (11) equipped with an adjustable valve. Two differential mechanisms and two reducers are arranged so that input shafts of the reducers are at the same time half axes of the first differential mechanism, while output shafts of reducers are half axes of the second differential mechanism. The differential allows distribution of rotation between half axes within range from zero to a speed of a drive shaft on one of the half axes which corresponds to interval from the speed of the drive shaft to zero on the other half axis. A rotation speed of the variator driven shaft can be adjusted by means of adjustable valves through which liquid is pumped by gear oil pumps driven with specified shafts of the mechanism.

EFFECT: variator allows to change value of torque within any given range.

2 dwg

FIELD: engines and pumps.

SUBSTANCE: invention relates to a hydromechanical transmission incorporating a split mechanical and hydrostatic drives and is designed to be used in agricultural tractors. The hydromechanical four-gear infinitely-variable transmission incorporates planetary mechanism (32) including three planetary trains (34, 36, 38), four clutches (C1, C2, C3, C4) and brake (48) to throw in reverse. First hydrostatic assembly (20) is in mesh with planetary mechanism second crown gear (R2). In the First and Fourth gears, second hydrostatic assembly (18) is in mesh with carrier (28) thrown in by first clutch (C1). In the Second and Third gears, second hydrostatic assembly is thrown into mesh with sun gear (S2) of the planetary mechanism second train by second clutch (C2). In the First and Second gears third clutch (C3) meshes carrier (28) with output shaft (46). In the Third and Fourth gears, fourth clutch (C4) meshes sun gear (S2) of the second planetary train with output shaft (46). Third planetary train (38) incorporates brake (48) to throw in reverse. When brake (48) meshes to throw in reverse and both clutches, third and fourth, (C3, C4), are disengaged, third train sun gear (S3) and, hence, transmission output shaft (46) runs reverse.

EFFECT: infinitely-variable transmission with steady efficiency in operating conditions.

27 cl, 6 dwg

FIELD: machine building.

SUBSTANCE: hydro-automatic output control gear incorporates input shaft 1 and output shafts 3, 4 coupled with propulsion unit and inter-jointed by differential 2, its output elements being coupled with pumps 10, 11 be planetary drive of hydraulic control system. Pumps 10, 11 communicate, via control valve 17, with common fluid flow rate control valve driven by both aforesaid output elements. Aforesaid control valve 17 is articulated to steering drive worm 18.

EFFECT: improved vehicle propulsion performances, better steering, longer life of propulsion unit due to automatic shut-off of fluid flow rate control valve.

2 dwg

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